CN110560737A

CN110560737A - hand-held power tool

Info

Publication number: CN110560737A
Application number: CN201910493422.XA
Authority: CN
Inventors: 郑悦; 张士松; 钟红风; 孙益民
Original assignee: Positec Power Tools Suzhou Co Ltd
Current assignee: Positec Power Tools Suzhou Co Ltd
Priority date: 2018-06-06
Filing date: 2019-06-06
Publication date: 2019-12-13
Anticipated expiration: 2039-06-06
Also published as: WO2019233482A1; CN110560717A; US20220055120A1; EP3808507A4; CN210589111U; EP3808507A1; CN210996564U; CN210188575U; CN110560738A; WO2019233485A1; CN110561359A; CN110560737B

Abstract

The present application relates to a hand-held power tool, the operating member being movable relative to the housing along a first trajectory between a first position corresponding to a first speed and a second position corresponding to a second speed, and the hand-held power tool being in a drill mode when the operating member is moved between the first position and the second position; when the operating member is located at the first position, the operating member can move along other tracks from the first position so as to switch the hand-held power tool from the drilling mode to the chuck adjusting mode. Among this application hand-held type power tool, the operating parts can be followed first orbit execution speed and switched over, and the operating parts just can be switched over to the chuck mode of regulation by the drilling mode under the low-speed mode simultaneously, avoids when the chuck mode of regulation, and when the rotational speed is higher, the quiet end tooth of separation and reunion moves the end tooth and meshes repeatedly and throw off and produce great noise with the separation and reunion.

Description

Hand-held power tool

Technical Field

The present invention relates to a hand-held power tool, and more particularly to a hand-held power tool having an automatic locking or automatic unlocking tool bit.

Background

Hand-held power tools, such as electric drills for drilling or screwing a workpiece (e.g., a wooden or concrete board or the like), have a spindle on which a collet for holding a tool bit is mounted. According to different functions of the hand-held power tool, tool heads with different specifications and types (such as a screwdriver head for screwing a screw, a flat drill capable of drilling on a wood board, a percussion drill capable of drilling on a cement board, a twist drill capable of drilling on a steel plate and the like) can be selected, when the tool heads are replaced or replaced, the chuck is firstly required to be opened or released, the original tool head is taken out from the opened chuck, and then the new tool head is inserted and then locked in the chuck.

The traditional hand-held power tool switches the tool between a working mode and a chuck adjusting mode with a replaceable working head through a mode switching mechanism, and comprises a motor, a driving shaft and a chuck, wherein the motor is positioned in a shell, the driving shaft is driven by the motor to rotate, the chuck is connected with the driving shaft, and an output planetary gear train and a clutch mechanism used for protecting the chuck after the chuck is opened or clamped in place are arranged in the chuck. The clutch mechanism comprises a first clutch piece fixedly connected with the output gear ring, a second clutch piece connected with the adjusting ring and capable of axially moving relative to the adjusting ring, and a clutch elastic element arranged at the front end of the second clutch piece.

When the clamping jaw is switched to a chuck adjusting mode, the output gear ring with the first clutch piece is driven by the mode operating piece to axially move so as to be connected with the second clutch piece in the rotating direction to drive the adjusting ring to rotate relative to the body, so that the clamping jaws are loosened or clamped. In the chuck adjusting mode, under the action of the clutch elastic element, the clutch static end teeth and the clutch moving end teeth are repeatedly engaged and disengaged, so that high noise is generated, and the noise is very harsh particularly at high rotating speed.

Disclosure of Invention

The present invention provides a hand-held power tool that reduces the "tripping" noise of a clutch mechanism during a chuck adjustment mode.

A hand-held power tool comprising:

A housing;

A motor disposed in the housing and outputting rotational power;

A transmission mechanism having a drive shaft capable of outputting power of the motor,

The chuck component comprises a body, a plurality of clamping jaws movably arranged relative to the body and an adjusting piece in threaded connection with the clamping jaws;

the operating part is movably assembled on the shell;

A mode selection mechanism capable of switching the hand-held power tool between at least a drilling mode and a chuck adjustment mode, the drive shaft driving the body, the jaws, and the adjustment member to rotate together when the hand-held power tool is in the drilling mode; when the hand-held power tool is in a chuck adjusting mode, one of the adjusting piece and the body can be driven by the motor to rotate relative to the other of the adjusting piece and the body so as to move the clamping jaws relative to the body to close or open; and

A high-low speed switching mechanism capable of switching the hand-held power tool between at least a first speed and a second speed greater than the first speed in response to the operation of the operating member and changing the rotation speed of the drive shaft;

The operating member can move between a first position corresponding to a first speed and a second position corresponding to a second speed along a first track relative to the machine shell, and when the operating member moves between the first position and the second position, the hand-held power tool is in a drilling mode; when the operating member is located at the first position, the operating member can move along other tracks from the first position so as to switch the hand-held power tool from the drilling mode to the chuck adjusting mode.

In one embodiment, the casing is provided with a sliding groove for the operating element to move, the sliding groove comprises a first sliding groove and a second sliding groove corresponding to the first track, and the second sliding groove is communicated with the first sliding groove at a first position, so that the operating element can move from the first position to the second sliding groove to switch the handheld power tool to a chuck adjusting mode.

in one embodiment, when the operating member moves from the first position to the preset position along the second sliding groove, the handheld power tool is switched to a chuck adjusting mode capable of opening the clamping jaws; the sliding groove further comprises a third sliding groove communicated with the first sliding groove at the first position, and when the operating piece moves to a preset position from the first position along the third sliding groove, the handheld power tool is switched to a chuck adjusting mode capable of folding the clamping jaws.

In one embodiment, the first sliding groove extends in the axial direction of the driving shaft on the housing, and the second sliding groove and the third sliding groove are symmetrically disposed on two sides of the first sliding groove.

in one embodiment, the transmission mechanism includes a speed change gear ring located between the motor and the body, the speed change gear ring is connected with the operating member and can move axially under the action of the operating member to enable the transmission mechanism to output at least two different transmission ratios so as to change the rotating speed of the driving shaft, and the hand-held power tool can be switched between a first speed and a second speed.

In one embodiment, the first slide groove extends in the axial direction of the drive shaft on the housing, and the high-low speed switching mechanism includes a slider drivingly connected between the operating member and the shift ring gear in the axial direction of the drive shaft;

When the operating part moves along the first sliding groove, the sliding part can move axially under the action of the operating part and drive the speed change gear ring to move; the sliding member is provided with a mode switching groove in the circumferential direction, and when the hand-held power tool is switched from a drilling mode to a chuck adjusting mode, the operating member can rotate relative to the sliding member and the speed change gear ring along the mode switching groove.

in one embodiment, the mode selection mechanism comprises a link and a locking member non-rotatably disposed relative to the housing, the link and the locking member being movable by the operator when the hand-held power tool is switched between a drill mode and a chuck adjustment mode;

when in a chuck adjustment mode, the locking member is coupled to the body and is capable of locking the body relative to the housing, and the coupling is capable of transmitting rotational power from the drive shaft to the adjustment member to rotate the adjustment member relative to the jaws.

in one embodiment, the handheld power tool further comprises an output sun gear connected with the driving shaft, an output planet gear arranged on the body and driven by the output sun gear, and the connecting piece is annular and provided with inner teeth meshed with the output planet gear on the inner peripheral surface;

When the drilling mechanism is in a drilling mode, the connecting piece disconnects power transmission between the output planetary wheel and the adjusting piece, and the locking element is disconnected with the body and is connected with the connecting piece in a rotation direction in a non-relative-rotation mode, so that the body is driven by the output planetary wheel to rotate and drive the adjusting piece to rotate together.

In one embodiment, the hand-held power tool further comprises an output sun gear connected with the drive shaft, an output planet gear arranged on the body and driven by the output sun gear, and an output ring gear meshed with the output planet gear;

When in a chuck adjusting mode, the output gear ring can rotate relative to the shell, and the connecting piece can transmit the rotary power of the output gear ring to the adjusting piece so that the adjusting piece can rotate relative to the clamping jaws;

When the drilling machine is in a drilling mode, the output gear ring is fixed relative to the machine shell, the connecting piece disconnects power transmission between the output gear ring and the adjusting piece, and the locking element is separated from the body, so that the body rotates under the driving of the output planetary gear and drives the adjusting piece to rotate together.

in one embodiment, the locking member is rotationally fixed with respect to the output ring gear in a direction of rotation to fix the output ring gear relative to the housing when in the drill mode.

In one embodiment, the operating member moves between a first position and a second position along a first track as a movement along the axial direction of the driving shaft, the mode selection mechanism further comprises a switching ring and a push rod assembly, the switching ring is provided with a guide groove, and when the handheld power tool is switched from a drilling mode to a chuck adjusting mode, the switching ring rotates around the axis of the driving shaft under the action of the operating member and drives the connecting member and the locking element to axially move through the guide groove and the push rod assembly.

In one embodiment, the switching ring is provided with a slot extending axially along the drive shaft, and the operating member is capable of moving axially along the slot when moving between the first position and the second position along the first track, so that the operating member is capable of moving axially along the drive shaft relative to the switching ring.

Among this application hand-held type power tool, the operating parts can be followed first orbit execution speed and switched over, and the operating parts just can be switched over to the chuck mode of regulation by the drilling mode under the low-speed mode simultaneously, avoids when the chuck mode of regulation, and when the rotational speed is higher, the quiet end tooth of separation and reunion moves the end tooth and meshes repeatedly and throw off and produce great noise with the separation and reunion.

Drawings

FIG. 1 is an exploded perspective view of a transmission mechanism and a corresponding area of an output device according to an embodiment of the present invention;

FIG. 2 is a perspective view of the screwdriver of FIG. 1;

FIG. 3 is a cross-sectional view of the screwdriver of FIG. 1 in a chuck adjustment mode with the jaws in a clamped condition;

FIG. 4 is a cross-sectional view of the screwdriver of FIG. 1 in a chuck adjustment mode with the jaws in a released state;

FIG. 5 is a cross-sectional view of the screwdriver of FIG. 1 in a drilling mode with the screwdriver in a low speed state;

FIG. 6 is a cross-sectional view of the screwdriver of FIG. 1 in a drilling mode, with the screwdriver in a high speed state;

FIG. 7 is an enlarged view of portion A of the screwdriver of FIG. 3;

FIG. 8 is a schematic view of the relationship between the operating member and the slot of the screwdriver of FIG. 1 with the jaws of the chuck adjustment mode in an open position;

FIG. 9 is a schematic view of the switching ring opening trigger triggering the motor reversing switch in a state corresponding to FIG. 8;

FIG. 10 is a schematic view of the relationship between the operating member and the slide slot when the screwdriver is in the low speed state in the drilling mode shown in FIG. 1;

FIG. 11 is a schematic view showing the relationship between the position of the switching ring and the position of the motor reversing switch in a state corresponding to FIG. 10;

FIG. 12 is a schematic view of the operating member and runner position relationship of the chuck adjusting mode jaws of the screwdriver of FIG. 1 in a locked condition;

FIG. 13 is a schematic view of the locking trigger of the shift ring triggering the motor reversing switch in a state corresponding to FIG. 12;

Fig. 14 is a perspective view of a second ring gear with a shift wire in the screwdriver of fig. 1;

FIG. 15 is a schematic view of the positional relationship of the gearbox housing, shift wire, operating members and shift ring of the screwdriver of FIG. 1;

FIG. 16 is a perspective view of an operating member and a slide member coupled to the operating member of the screwdriver of FIG. 1;

FIG. 17 is a perspective view of a switching ring of the screwdriver of FIG. 1;

FIG. 18 is a perspective view of another structure within the housing of the screwdriver of FIG. 1 in a low speed state during a drill mode of the screwdriver;

FIG. 19 is another perspective view of the interior of the housing of FIG. 1 with the screwdriver in a high speed state during a drill mode;

FIG. 20 is a perspective view of another structure in the housing corresponding to FIG. 8;

FIG. 21 is a perspective view of another structure in the housing corresponding to FIG. 12;

FIG. 22 is a perspective view of the output ring gear of the screwdriver of FIG. 1 and a second push rod assembly connected thereto;

FIG. 23 is a perspective view of the body lock of the screwdriver of FIG. 1 and the first push rod assembly coupled thereto;

FIG. 24 is a partially exploded perspective view of the drive mechanism and chuck assembly of the second embodiment of the present invention;

FIG. 25 is a cross-sectional view of a second embodiment of the present invention with the screwdriver in a drilling mode;

FIG. 26 is a cross-sectional view of a second embodiment of the present invention with the screwdriver in a chuck adjusting mode;

FIG. 27 is a partial cross-sectional view of a third embodiment of the present invention with the screwdriver in drilling mode;

FIG. 28 is a partial cross-sectional view of an intermediate state of the third embodiment of the present invention with the driver switched from the drill mode to the chuck adjustment mode;

FIG. 29 is a partial cross-sectional view of an intermediate state of the third embodiment of the present invention with the driver switched from the drill mode to the chuck adjustment mode;

FIG. 30 is a partial cross-sectional view of a third embodiment of the present invention with the screwdriver in a chuck adjustment mode;

FIG. 31 is an exploded perspective view showing a partial structure of a screwdriver according to a fourth embodiment of the present invention;

FIG. 32 is a schematic cross-sectional view of a fourth embodiment of the present invention illustrating a driver in a drill mode;

FIG. 33 is a schematic view of a portion of a fourth embodiment of the present invention illustrating a screwdriver in a drilling mode;

FIG. 34 is a schematic cross-sectional view of a fourth embodiment of the present invention showing a screwdriver in chuck adjustment mode;

FIG. 35 is a schematic view of a portion of a fourth embodiment of the present invention in a chuck adjustment mode;

FIG. 36 is a schematic structural diagram of a screwdriver according to a fourth embodiment of the present invention;

FIG. 37 is a schematic cross-sectional view showing a partial structure of a screwdriver in a chuck adjustment mode in accordance with a fourth embodiment of the present invention;

FIG. 38 is a schematic cross-sectional view showing a partial structure of a screwdriver in a chuck adjustment mode in accordance with a fourth embodiment of the present invention;

FIG. 39 is a schematic cross-sectional view showing a partial structure of a driver in a drilling mode according to a fourth embodiment of the present invention;

FIG. 40 is a schematic view of a partial structure of a screwdriver according to an embodiment of the present disclosure, wherein the mode selector is located at the second position, the first abutting portion abuts against the first limiting arm, and the first limiting arm is adapted to drive the limiting mechanism to pivot in a predetermined direction;

FIG. 41 is a schematic view of a portion of a screwdriver in accordance with an embodiment of the present invention, wherein as the mode selector continues to move in the first direction, the mode selector continues to push the interlock unit to rotate, and the second arm will abut against the switch trigger;

FIG. 42 is a schematic view of a portion of a screwdriver in accordance with an embodiment of the present invention, wherein the switch trigger is moved along a first direction to an end position, and the first position-limiting arm abuts against the mode-selecting member;

FIG. 43 is an axial cross-sectional view of a fifth embodiment of the present invention showing the screwdriver in the low speed position in the drill mode;

FIG. 44 is a top cross-sectional view of a fifth embodiment of the present invention with the screwdriver in the low speed position for drilling mode;

FIG. 45 is an axial cross-sectional view of a fifth embodiment of the present invention with the screwdriver in the drill mode high speed position;

FIG. 46 is a top cross-sectional view of a fifth embodiment of the present invention, with the screwdriver in the drill mode high speed position;

FIG. 47 is an axial cross-sectional view of a fifth embodiment of the present invention showing the screwdriver in an intermediate state when switching from the drill mode high speed position to the chuck adjustment mode;

FIG. 48 is a top cross-sectional view of a fifth embodiment of the present invention showing the screwdriver in an intermediate position during a transition from the drill mode to the chuck adjustment mode;

FIG. 49 is an axial cross-sectional view of a fifth embodiment of the present invention, showing a screwdriver in a chuck adjusting mode;

FIG. 50 is a top cross-sectional view of a fifth embodiment of the present invention, showing a screwdriver in a chuck adjusting mode;

FIG. 51 is a schematic view of the combination of the speed selecting member and the mode selecting member of the screwdriver in the fifth embodiment of the present invention;

FIG. 52 is a schematic view of a speed selector for a screwdriver according to a fifth embodiment of the present invention;

FIG. 53 is a schematic structural diagram of a knob of a screwdriver according to a fifth embodiment of the present invention.

Detailed Description

In the preferred embodiment of the hand-held power tool of the present invention, the hand-held power tool is a screwdriver, which can be divided into a pneumatic screwdriver, a hydraulic screwdriver and an electric screwdriver according to the power source, and the electric screwdriver is divided into a dc screwdriver and an ac screwdriver.

Referring to fig. 1-6, a dc powered screwdriver 10 includes a housing, a motor 12 positioned within the housing to output rotational power, a battery 18 for supplying power, a transmission, a chuck assembly including a chuck housing 1104, and an output device 15 positioned at least partially within the chuck housing 1104.

the casing includes a handle portion to be gripped and a body portion for housing the motor. The handle portion is disposed at an angle to the main body portion, and the handle portion includes a handle housing 1102 for forming a grip handle, and the main body portion includes a main housing 1101 fixedly connected to the handle housing 1102 and operable to support and cover the motor 12. Specifically, main housing 1101 is a horizontally extending cylindrical structure formed by abutting cartridge housing 1104 (front housing) with rear housing 1103. In this embodiment, the main housing 1101 and the handle housing 1102 are disposed at an obtuse angle K, preferably between 100 degrees and 130 degrees, so that the handle can be held comfortably. In this embodiment, the main housing 1101 and the handle housing 1102 are disposed at an obtuse angle K, preferably between 100 degrees and 130 degrees, so that the handle can be held comfortably. The main housing 1101 has a rear end surface located at the rear (the front and rear directions mentioned in the present invention refer to the front and rear directions of the hand-held power tool shown in fig. 4 as the reference standard, that is, the direction from the rear to the front is the direction from the motor to the output device 15), and a front end surface located at the front, and the main housing 1101 sequentially accommodates the motor 12, the transmission mechanism, and at least a part of the output device 15 from the rear end surface to the front end surface. Preferably, the handle housing 1102 and the rear housing 1103 are both composed of a half housing, and the half housing of the rear housing 1103 and the half housing of the handle housing 1102 are integrally formed, and the cartridge housing 1104 is a cylindrical housing (see fig. 1). It will be appreciated that in other embodiments, the cartridge housing 1104 may be comprised of two half housings, or the half housings of the cartridge housing 1104, the rear housing 110, and the handle housing 1102 on the same side may be integrally formed to form two symmetrical half housings that comprise a housing. It will be appreciated, of course, that in other embodiments, the collet housing 1104 may be configured to rotate relative to the rear housing 1103, such as when the power tool is being used to make work hours, and the collet housing 1104 rotates with the output device 15

a push button switch 19 is provided in a portion of the upper portion of the handle case 1101 adjacent to the main case 1101, and a battery 18 is fixed to the rear portion of the handle case 1101. As a preferred embodiment, the battery 18 may be a lithium ion battery. It should be noted that the lithium ion battery referred to herein is a generic term of a rechargeable battery based on lithium ion extraction-incorporation reaction, and may be constructed in many systems, such as "lithium manganese" battery, "lithium iron" battery, etc., depending on the positive electrode material. Of course, the battery may be other types of batteries, such as nickel cadmium, nickel metal hydride, and the like, as would be known to one skilled in the art.

The transmission mechanism comprises at least one stage of variable speed planetary gear train, the variable speed planetary gear train comprises a variable speed gear ring positioned between the motor 12 and the body 151, and the variable speed gear ring can move between a first variable speed position and a second variable speed position along the axial direction of the driving shaft under the action of external force so as to enable the transmission mechanism to output at least two different transmission ratios, thereby changing the rotating speed of the driving shaft and further enabling the handheld power tool to be switched between the first speed and the second speed. When in the first gear position, the transmission mechanism can output in a first transmission ratio; when in the second shift position, the transmission mechanism is capable of outputting at a second gear ratio that is greater than the first gear ratio.

In this embodiment, the transmission mechanism is specifically a planetary gear speed reduction mechanism 13, which has a driving shaft capable of outputting the power of the motor 12, so that the rotational motion output by the output shaft of the motor 12 is reduced by the planetary gear speed reduction mechanism 13 and then transmitted to the output device 15, and the output device 15 further drives the tool bit to rotate, so that the tool bit is output at a required speed.

With continued reference to fig. 1-6, in the preferred embodiment of the present invention, the motor 12 is a motor, which is fixed in the rear housing 1103 by a positioning rib (not shown) in the housing and a screw 17, etc., and the motor has a motor shaft 121 extending forward from the rear housing 1103, and the motor shaft 121 extends into the planetary gear reduction mechanism 13 and is output after being reduced in speed by the planetary gear reduction mechanism 13. Preferably, the planetary gear reduction mechanism 13 is a two-stage planetary gear reduction mechanism including a first-stage planetary gear train 131 near the motor, and a second-stage planetary gear train 132 near the output device 15. The first stage planetary gear train 131 includes a first sun gear 1310 fixed on the motor shaft 121, a first planet gear 1311 engaged with the first sun gear 1310 and disposed at an outer circumference of the first sun gear 1310, a first ring gear 1312 engaged with the first planet gear 1311, and a first carrier 1313 for supporting the first planet gear 1311, and the second stage planetary gear train 132 includes a second sun gear 1320 fixed on the first carrier 1313, a second planet gear 1321 engaged with the second sun gear 1320, a second ring gear 1322 engaged with the second planet gear 1321, and a second carrier 1323 for supporting the second planet gear 1321.

The output device 15 includes an output shaft 150, the output shaft 150 includes a body 151, a clamping groove 153 disposed in the body 151 and forming a certain angle with respect to an axis of the output shaft 150, and an accommodating hole for accommodating a tool bit, the output device 15 further includes a clamping jaw disposed in the clamping groove and surrounding the accommodating hole to clamp the tool bit, and an adjusting member sleeved on an outer periphery of the body 151. In this embodiment, the diameter of the receiving hole is not less than 10mm, and preferably, the diameter of the receiving hole is between 10mm and 13 mm.

Preferably, the adjusting ring comprises a nut sleeve 154, an internal thread (not shown) is provided on the inner circumferential wall of the nut sleeve 154, and an external thread 1521 is provided on the side of the clamping jaw 152 facing the internal thread, and when the nut sleeve 154 is rotated relative to the clamping jaw 152, the clamping jaw 152 performs an opening or closing action due to the interaction between the internal thread and the external thread 1521. Preferably, a nut sleeve 154 is rotatably but axially immovably disposed on the body 151. Preferably, the body 151 is provided with an annular groove 1511 on the outer periphery, the nut sleeve 154 is rotatably disposed in the annular groove (not shown), and the annular groove can limit the nut sleeve 154 from moving axially.

referring to fig. 7, the body 151 includes a first flange 1512 and a second flange 1513 respectively located at two ends of the annular groove, wherein the first flange 1512 can abut against an end of the nut sleeve 154 close to the tool head to limit the movement of the nut sleeve 154 toward the end of the tool head (i.e., forward movement), and the second flange 1513 can axially limit an end of the nut sleeve 154 close to the motor 12 to prevent the nut sleeve 154 from moving toward the direction close to the motor (i.e., backward movement). It will be appreciated that when the jaws 152 clamp or nearly clamp against the tool head, the force from the jaws 152 (jaw threads) increases as the nut sleeve 154 rotates, and the nut sleeve 154 has a tendency to move axially rearward, i.e., the nut sleeve 154 will subject the second flange 1513 to a greater rearward axial force, and for this purpose, an end bearing 155 and a shim 156 are provided between the nut sleeve 154 and the second flange 1513, preferably the shim 156 is a wear resistant metal shim. In this embodiment, in order to facilitate installation, the nut sleeve 154 is formed by splicing two semicircular half nut sleeves, but in other embodiments, the nut sleeve 154 may be provided in a manner of 3 or more than three half nut sleeves. It will be appreciated that in order to effectively secure the two nut half shells together, the outer side of the two nut half shells is fitted with a nut sleeve 157.

Referring to fig. 5 and 6, in the present embodiment, the second ring gear 1322 (i.e., equivalent to the shift ring gear in the present embodiment) is movable along the motor output shaft 121 with respect to the housing between a first shift position (see fig. 6) close to the motor and a second shift position (see fig. 5) remote from the motor. When the second ring gear 1322 is located at the first shift position, the second ring gear 1322 is rotatably disposed in the housing, and the second ring gear 1322 is engaged with the first planet carrier 1313 and the second planet gear 1321 at the same time, so that the first planet carrier 1313, the second planet gear 1321 and the second ring gear 1322 rotate together, the second-stage planetary gear set 132 does not output a reduced speed, that is, the second planet carrier 1323 rotates at the same speed as the first planet carrier 1313, and the second planet carrier 1323 outputs a high speed. When the second ring gear 1322 is located at the second shift position, the second ring gear 1322 is circumferentially fixed to the rear housing 110 in a non-rotatable manner, and the second ring gear 1322 is disengaged from the first carrier 1313 during the axial movement but the second ring gear 1322 remains engaged with the second planet gears 1321, so that the second carrier 1323 is output at a predetermined reduction gear ratio with respect to the first carrier 1313, and the second carrier 1323 outputs a low speed.

Referring to fig. 1 and 5, the first planet carrier 1313 includes a first pin (not labeled) for mounting the first planet 1311, a first planet carrier body 1314, and a first planet carrier output shaft 1315 disposed on a surface of the first disc-shaped body 1314 facing away from the first pin. In this embodiment, the screwdriver further includes a gearbox housing located outside the first-stage planetary gear train 131 and the second-stage planetary gear train 132 and used for enclosing the first-stage planetary gear train 131 and the second-stage planetary gear train 132, preferably, the gearbox housing includes a gearbox rear end cover 1121 for isolating the motor from the first-stage planetary gear train 131, a gearbox sleeve 1122 circumferentially surrounding the outside of the first-stage planetary gear train 131 and the second-stage planetary gear train 132, and a front end cover 1123 located between the second-stage planetary gear train 132 and the output device 15, a hollow support sleeve 1124 (see fig. 1 or fig. 3) extending towards the inside of the output device 15 is axially arranged in the middle of the front end cover 1123, a driving shaft 1325 of the second planet carrier 1323 is rotatably arranged in the support sleeve 1124 and extends to the inside of the output device 15, therefore, the hollow support sleeve 1124 can support the driving shaft 1325 of the second planet carrier 1323 well, so that the output of the second stage planet carrier 1323 is more stable. In other embodiments, a second rotation support 1327, such as a needle bearing or an oil bearing, may be further disposed between the outer wall of the driving shaft 1325 of the second planet carrier 1323 and the inner wall of the support sleeve 1324. Preferably, in order to better support the output device 15, the body 151 is rotatably supported outside the supporting sleeve 1324, and in other embodiments, a third rotating supporting member 1328 may be further disposed between the supporting sleeve 1324 and the body 151. In order to achieve support for the output device 15 and the second planet carrier 1323 without increasing the axial length of the hand held power tool for ease of handling and operation, the portion of the support sleeve 1324 supporting the second planet carrier 1323 and the portion of the support sleeve 1324 supporting the output device 15 at least partially axially overlap or the second rotary support 1327 and the third rotary support 1328 at least partially axially overlap. Preferably, in this embodiment, a distance L1 from a side surface of the rear end cover close to the transmission mechanism to a side surface of the output shaft 150 far from the motor is not greater than 80mm, and in this embodiment, a total length is not greater than 145mm, that is, an axial length L2 between the tail end of the main housing 1101 and an outer side surface of the output shaft 150 close to the head end of the main housing is not greater than 145 mm. In this embodiment, in order to further support the output device 15, that is, the main body 151, a first rotary support 16 is disposed between the main body 151 and the front housing 1104 to support the main body 151, preferably, the first rotary support 16 is a support bearing, and the output device 15 is under the action of the first rotary support 16 and the third rotary support 1328, so that the output of the output shaft 150 is more stable and the working precision is higher. The first rotating support member 16 has an inner end near the adjustment ring and an outer end far from the adjustment ring, and the outer end is flush with the head end of the main housing 1101.

in this embodiment, the output device 15 further includes an output planet wheel 1581 rotatably fixed on the body 151, and an output ring gear 1582 located outside the output planet wheel 1581 and engaged with the output planet wheel 1581, and an output sun wheel 1583 engaged with the output planet wheel 1581 is disposed on the driving shaft 1325. In this embodiment, in order to facilitate the manufacturing of the output device 15, the body 151 includes a first body 151a and a second body 151b rotatably connected to the first body 151a, and in order to meet the strength requirement for torque transmission between the first body 151a and the second body 151b, preferably, one of the first body 151a and the second body 151b extends toward the other body to form an extending portion 151c at least partially axially overlapping with the other body, and performs torque transmission by circumferential abutment of the overlapping portion of the first body 151a and the second body 151b, and the first body 151a and the second body 151b are fixedly connected by press fitting. The first body 151a is located between the planetary gear reduction mechanism 13 and the output planet 1581.

Referring to fig. 1 and 4, in order to further shorten the axial length of the hand-held power tool, the projection of the clamping groove 153 on the axis of the output shaft 150 at least partially overlaps the projection of the output planet on the axis of the output shaft 150, i.e., the clamping groove 153 is at least partially located on the extension 151 c. Preferably, the projection of the clamping groove 153 on the axis of the output shaft 150 is at least partially axially overlapped with the projection of the first body 151a on the axis of the output shaft 150, i.e. the clamping groove 153 is at least partially disposed on the first body 151a to provide a space for the clamping jaw 153 to move in the motor direction when opened.

Referring to fig. 6, in this embodiment, the output device 15 further includes an output pin 1584 (see fig. 6) fixed on the body 151, and the output planet 1581 is rotatably disposed on the output pin 1584. Preferably, to facilitate the assembly of the output device 15, the output pin 1584 is selectively fixed to the first body 151a or the second body 151b, in this embodiment, preferably, one end of the output pin 1584 close to the first body 151a is fixed to the first body 151a, and one end of the output pin 1584 close to the second body 151b is spaced apart from the second body 151b, that is, one end of the output pin 1584 close to the second body 151b is in a suspended state and is not fixed to the second body 151 b. To reduce friction between the end of the output planet 1581 and the first body 151a or the second body 151b, a washer 1337 (see fig. 1 and 7) is provided between the output planet 1581 and the first bodies 151a and 151b, and preferably, the washer 1337 is a metal washer. It should be noted that the output pin 1584 may also be fixed on the second body 1335, or one end of the output pin 1584 is fixed on the first body 151a, and the other end is fixed on the second body 151 b. It is understood that in other embodiments, the structure of the output device 15 may be in other forms, and will not be described herein.

An output sun gear 1583 is located on a second planet carrier drive shaft 1325 which extends outside the hollow support sleeve 1124 and meshes with output planet gears 1581 provided on the body 151 to transmit the rotation of the second stage planetary gear train 132 to the output means 15. In the present embodiment, the output ring gear 1332 has a first operating position axially close to the motor and a second operating position away from the motor, referring to fig. 4-5, when the screwdriver is in the drill mode and the output ring gear 1582 is in the first operating position, the output ring gear 1582 is non-rotatably fixed relative to the machine case, that is, the output ring gear 1582 is non-rotatably fixed relative to the machine case, and the output ring gear 1582 is meshed with the output planet gears 1581. Therefore, the output sun gear 1583 transmits rotation to the output planet gear 1581, and the output planet gear 1581 drives the body 151, the clamping jaw and the tool head located in the body 151 to rotate under the action of the fixed output inner gear 1582.

Referring to fig. 3-4, when output ring gear 1582 is in the second operating position when the screwdriver is in auto chuck mode, output ring gear 1582 is still meshed with third planet gears 1331 but is rotatable relative to the housing, i.e., when output ring gear 1582 is in the second operating position, output planet gears 1581 transmit rotation to output ring gear 1582, causing output ring gear 1582 to rotate relative to the housing. In the second working position, the output annulus gear 1582 is simultaneously able to transmit rotation to the nut sleeve 154 to rotate the nut sleeve 154 relative to the jaws 152, enabling the jaws 152 to perform opening or closing actions as required.

As can be seen from the above description, in the auto chuck mode, when the output ring gear 1582 is located at the second working position, the output planet gears 1581 transmit the rotation to the output ring gear 1582 and further transmit the rotation to the nut sleeves 154 through the output ring gear 1582 so that the nut sleeves 154 rotate relative to the body 151 (the clamping jaws 152) which does not rotate at this time, so that the clamping jaws 152 perform the opening or closing action as required. The present embodiment preferably enables the nut sleeve 154 to rotate relative to the body 151 and the jaws 152 disposed within the body 151 by selectively locking the body 151 (i.e., the cartridge body) to the housing, and preferably secures the body 151 relative to the housing by selectively locking the first body 151a to the housing.

The screwdriver 10 further includes an operating member 30 and a mode selection mechanism. Wherein the operating member 30 is movably mounted on the housing, and the mode selection mechanism is capable of switching the hand-held power tool (screwdriver) between at least a drill mode (hereinafter referred to as drill mode) and a chuck adjustment mode (hereinafter referred to as auto chuck mode) in response to operation of the operating member 30.

When the screwdriver is in the drill mode, the driving shaft drives the body 151, the clamping jaw 152, the nut sleeve 154 (adjustment member) and the tool head (screwdriver head) to rotate together to perform work; when the screwdriver is in the auto chuck, one of the nut sleeve 154 and the body 151 can be rotated relative to the other by the motor 12 to move the plurality of jaws 152 relative to the body 151 to close or open. In this embodiment, the body 151 and the jaws 152 within the body 151 are not rotated, and the nut sleeve 154 is rotated relative to the jaws 152 to cause the jaws 152 to perform an opening or closing motion.

Referring to fig. 1, to achieve the fixation of the first body 151a relative to the casing in the auto chuck mode and the fixation of the output ring gear 1582 relative to the casing in the drill mode, the mode selection mechanism includes a link (i.e., the body lock 134 in the first embodiment) and a locking member (i.e., the ring gear lock 181 in the first embodiment) that is non-rotatably provided relative to the casing.

the coupling and locking member are movable by the operator 30 when the hand-held power tool is switched between the drilling mode and the chuck adjustment mode;

When in the chuck adjustment mode, the locking member is coupled to the body 151 and is capable of locking the body relative to the housing, and the coupling is capable of transmitting rotational power from the drive shaft to the adjustment member (nut sleeve 154) to rotate the adjustment member relative to the jaws 152.

specifically, the mode selection mechanism includes a locking member 130 (formed by a connecting member integrally provided with a locking member) for fixing the first body 151a, the locking member 130 is fixed to the housing in a non-rotatable manner all the time in the circumferential direction, but can move axially relative to the housing to switch between a first locking position and a second locking position, preferably, in the present embodiment, the locking member 130 is moved in the axial direction to switch between the first locking position and the second locking position, and the first locking position is close to the first body 151a and the second locking position is far from the first body 151 a. Referring to fig. 3 and 4, when the screwdriver is in the auto chuck mode, the locking member 130 is located at the first locking position, and the locking member 130 circumferentially non-rotatably locks the first body 151a to the housing. Referring to fig. 4-5, when in the drill mode, the locking element 130 is located at the second locking position, the locking element 130 releases the circumferential locking of the first body 151a, and the output planet 1581 can drive the body 151 and the clamping jaws 152 located in the body 151 to rotate together. It should be noted that, as can be seen from the above description, in this embodiment, since output ring gear 1582 is in the first position that is not rotatable relative to the housing in the drill mode, the mode selection mechanism further includes a structure for fixing output ring gear 1582 to the housing in the first working position, such as an inner ring gear lock, in this embodiment, in order to simplify the structure inside the screwdriver, locking member 130 can also be used for circumferentially fixing output ring gear 1582, that is, in this embodiment, locking member 130 simultaneously functions as an inner ring gear lock, that is, locking member 130 includes body lock 134 (i.e., a connecting member) for locking the body and inner ring gear lock 181 (i.e., a locking member) for locking output ring gear 1582.

The structure of the locking member 130 and the operation principle of how the locking member 130 functions as the body lock 134 and the inner ring gear lock 181 in the drill mode and the auto chuck mode, respectively, will be described in detail with reference to the accompanying drawings. Referring to fig. 4-5, in drill mode, when locking member 130 is in the second lock position, output annulus 1582 is in the first operating position. At this time, the locking member 130 (body lock 134, i.e., a connecting member) releases the circumferential locking of the first body 151a, and is simultaneously connected with the output ring gear 1582 and non-rotatably fixes the output ring gear 1582 to the casing, so that the output planet gears 1581 can drive the body 151 and the clamping jaws 152 to rotate, i.e., the body lock 134 is separated from the first body 151a, and the ring gear lock 181 (i.e., a locking member) is connected with the output ring gear 1582. Preferably, inner ring gear lock 181a includes through groove 1340 disposed on the inner wall of locking member 130, output ring gear 1582 is provided with ring gear locking teeth 1582a engaged with through groove 1340, circumferential fixing of output ring gear 1582 is achieved by above through groove 1340 of body lock 134 and ring gear locking teeth 1582a located at the end of output ring gear 1582, that is, ring gear locking teeth 1582a of output ring gear 1582 are inserted into corresponding axial through groove 1340 to achieve fixing of output ring gear 1582. At this time, the output sun gear 1583 transmits torque to the third planet gear 1331, and under the action of the output ring gear 1582, the output planet gear 1581 revolves around the output sun gear 1583 to drive the body 151 and the clamping jaws 152 to rotate, and the tool head is driven by the clamping jaws 152 to work.

In one embodiment, the hand-held power tool includes an output sun gear 1580 connected to the drive shaft and an output planet gear 1581 provided on the body 151 and driven by the output sun gear 1580. The connecting member (i.e., the body lock 134) is annular and has inner teeth on its inner peripheral surface that mesh with the output planet 1581.

when in the drilling mode, the connecting member disconnects the power transmission between the output planet 1581 (i.e., the driving shaft) and the adjusting member (i.e., the nut sleeve 134), the locking member (i.e., the inner ring lock 181) is disconnected from the body 151, and the connecting member is connected with the body 151 in a rotation direction without relative rotation, so that the body 151 is rotated by the output planet 1581 and drives the adjusting member to rotate together. That is, in this embodiment, the output planetary gears 1581 correspond to the output ring gear 1582, and force transmission between the driving shaft and the adjusting member, and between the driving shaft and the body 151 is achieved.

When the chuck adjusting mode is adopted, the output planet gears 1581 are meshed with the connecting pieces through internal teeth and can rotate relative to the machine shell, and the connecting pieces can transmit the rotating power of the output internal gear 1582 to the adjusting pieces so that the adjusting pieces can rotate relative to the clamping jaws 152.

In another embodiment, the hand-held power tool further comprises an output sun gear 1580 connected to the drive shaft, output planet gears 1581 provided to the body 151 and driven by the output sun gear 1580, and an output ring gear 1582 meshed with the output planet gears 1851.

When the clamping head adjusting mode is adopted, the output inner gear ring 1582 can rotate relative to the machine shell, and the connecting piece can transmit the rotating power of the output inner gear ring 1582 to the adjusting piece so that the adjusting piece can rotate relative to the clamping jaw 152;

When in the drilling mode, the locking element is disengaged from the body 151 and connected to the output annulus 1582 in a direction of rotation without relative rotation, so that the output annulus 1582 is fixed relative to the casing; meanwhile, the connecting member disconnects power transmission between the output inner gear ring 1582 and the adjusting member, and is connected with the body 151 in a rotation direction in a non-relative rotation manner, so that the body 151 rotates under the drive of the output planet wheel 1581 and drives the adjusting member to rotate together.

of course, it is understood that in other embodiments, the body lock 134 and the locking element coupled to the body lock 134 may have other forms, and will not be described herein.

when the screwdriver is switched from the drill mode to the auto chuck mode through the mode selection mechanism, at this time, the locking member 130 moves (moves backward) from the second lock position to the first lock position in a direction approaching the first body 151a to lock the first body 151a, and the output ring gear 1582 moves (moves forward) from the first working position to the second working position in a direction away from the first body 151a and approaching the nut sleeve 154 to realize separation from the inner ring gear lock 181a and rotational connection with the nut sleeve 154. Preferably, the first body 151a is provided with a first locking member coupled with the body lock 134, in this embodiment, the first locking member is a lock block 1510 disposed on the first body 151a, and the body lock 134 is provided with a second locking member coupled with the first locking member, preferably, the second locking member is the through groove 1340, that is, the locking member 130 (the body lock 134) is coupled with the lock block 1510 through the through groove 1340 to lock the first body 151 a. Therefore, in the auto chuck mode, when the locking member 130 is located at the first locking position, the output ring gear 1582 is located at the second working position, at this time, the locking member 130 circumferentially locks the body 151 and the clamping jaws 152, and the output ring gear 1582 drives the nut sleeve 154 to rotate relative to the clamping jaws 152.

referring to fig. 1 and 6, in the present embodiment, in the auto chuck mode, in order to ensure that the clamping jaws 152 are no longer clamped or opened after the clamping jaws 152 clamp the tool head or the clamping jaws 152 are loosened, that is, the nut sleeve 154 is no longer twisted on the clamping jaws 152, a clutch mechanism 20 for disconnecting the torque transmission between the output ring gear 1582 and the nut sleeve 154 after the clamping jaws 152 are clamped or completely opened is arranged between the output ring gear 1582 and the nut sleeve 154. The clutch mechanism 20 includes a first clutch member 21 rotatably connected to the output ring gear 1582, and a second clutch member 22 rotatably connected to the nut sleeve 154 and axially movable relative to the nut sleeve 154, wherein, when the clamping jaws 152 are clamped or fully opened, the second clutch member 22 is axially moved forward, the first clutch member 21 is disengaged from the second clutch member 22, and the output ring gear 1582 no longer transmits torque to the nut sleeve 154. Preferably, the first clutch member 21 is a snap ring sleeved on the periphery of the body 151, wherein one end of the snap ring near the output ring gear 1582 is provided with engaging teeth 211 matched with the inner teeth of the output ring gear 1582 to realize torque transmission, and one end of the snap ring near the second clutch member 22 is provided with a clutch moving end tooth 212 for performing torque transmission with the second clutch member 22. The second clutch member 22 is provided with a static clutch end tooth 222 cooperating with the dynamic clutch end tooth 212, and the front end of the second clutch member 22 is provided with a resilient clutch element 23, so that when the clamping jaw 152 is clamped or completely opened, i.e. the torque force between the first clutch member 21 and the second clutch member 22 is increased to a predetermined value, the second clutch member 22 compresses the resilient clutch element 23 to disengage the dynamic clutch end tooth 212 and the static clutch end tooth 222. After the second clutch member 22 is disengaged from the first clutch member 21, the second clutch member 22 is moved backward by the clutch elastic member 23, that is, automatically reset and pushes the second clutch member 22 to a position where the clutch moving end teeth 212 and the clutch stationary end teeth 222 are engaged. Therefore, when the jaws 152 are clamped or fully opened, the clutch mechanism 20 performs repeated automatic tripping operations.

Referring to fig. 1, the clutch movable end teeth 212 and the clutch stationary end teeth 222 include guide slopes (not shown) by which the second clutch member 22 can compress the clutch elastic member 23 to separate the first clutch member 21 and the second clutch member 22. It should be noted that, after the clamping jaws 152 are clamped or completely opened, the guiding inclined surface can make the first clutch member 21 have a tendency to move toward the motor, that is, the first clutch member 21 is subjected to an axial force of backward movement, in order to prevent the first clutch member 21 from moving backward to press the output ring gear 1582 (it should be noted that, when the output ring gear 1582 is subjected to an axial force from the first clutch member during tripping, that is, the clutch force, the output ring gear 1582 can also give an axial force to the mode selection mechanism driving the output ring gear 1582 to move, for example, an axial force is given to the operating member 30 (see the following description) driving the output ring gear 1582 to move, so that the operating member 30 is subjected to a force), the screwdriver 10 further includes an axial abutting member axially abutting against the first clutch member 21. Preferably, the axial abutment is a third flange 1514 (see fig. 7) provided on the body 151.

The operating member 30 of the mode selection mechanism and the structure associated with the operating member 30 in the present embodiment will be further described below with reference to fig. 8 to 23. As can be seen from the above description of the "tripping" principle of the clutch mechanism 20 in the auto chuck mode, the clutch static end teeth 222 and the clutch movable end teeth 212 repeatedly engage and disengage under the action of the clutch elastic element 23, which generates a loud noise, and the noise is very loud especially at high rotation speeds. In the present embodiment, the arrangement of the slide slot in the mode selection mechanism for movement of the operating member 30 enables the screwdriver to be in the automatic mode only in the low speed mode.

referring to fig. 8-13, the screwdriver 10 further includes a high-low speed switching mechanism that is capable of switching the hand-held power tool between at least a first speed and a second speed greater than the first speed in response to operation of the operating member 30 and changing the rotational speed of the drive shaft. Specifically, the operating member 30 is movable relative to the housing along a first trajectory between a first position corresponding to a first speed and a second position corresponding to a second speed, and the hand-held power tool is in the drill mode when the operating member 30 is moved between the first position and the second position; when the operating member 30 is in the first position, the operating member 30 can move along other tracks from the first position to switch the hand-held power tool from the drilling mode to the chuck adjusting mode.

in this embodiment, the casing is provided with a sliding slot for the operation member 30 to move, and the sliding slot includes a first sliding slot 311 and a second sliding slot 312 corresponding to the first track. The first link 311 allows the operating member 30 to be switched between a first position (low speed position) and a second position (high speed position) in the drill mode of operation. When the operating member 30 slides between the first position and the second position, the second annular gear 1322 can be driven to correspondingly move between the first speed changing position and the second speed changing position, so as to realize the high-speed and low-speed switching of the handheld power tool in the drill operating mode.

The second slide groove 312 is communicated with the first slide groove 311 at the first position, and the operating member 30 can move from the first position to the second slide groove 312, so that the hand-held power tool is switched to the chuck adjusting mode. Specifically, the second link 312 is coupled to the first position (i.e., the low speed position) of the first link 311 such that the operating member 30 is movable along the second link 312 to switch from the drill mode to the auto-chuck mode only when in the low speed position. In this embodiment, when the operating member 30 moves from the first position to the predetermined position along the second slide channel 312, the hand-held power tool switches to the chuck adjustment mode in which the jaws 152 are opened.

Preferably, the slide slot further comprises a third slide slot 313 communicating with the first slide slot 311 at the first position, and the operating member 30 is movable from the first position to the third slide slot 313 to switch the hand-held power tool to the chuck adjusting mode. Specifically, the third link 313 is coupled to the first position (i.e., the low speed position) of the first link 311 such that the operating member 30 is movable along the third link 313 to switch from the drill mode to the auto-chuck mode only when in the low speed position. In this embodiment, when the operating member 30 moves from the first position to the predetermined position along the third sliding slot 313, the hand-held power tool switches to the chuck adjusting mode in which the clamping jaws 152 can be closed.

That is, the second sliding slot 312 and the third sliding slot 313 are respectively disposed on both sides of the first sliding slot 311, and are connected to the first position in the first sliding slot 311, so as to respectively clamp and unclamp the clamping jaws 152 in the auto chuck mode. Preferably, the first sliding slot 311 extends along the axial direction of the motor shaft 121 on the housing, and the second sliding slot 32 and the third sliding slot 313 are distributed on both sides of the first sliding slot 311 and are substantially perpendicular to the first sliding slot 311. Thus, the chute is generally a "T" slot arrangement on the housing.

referring to fig. 14-16, in the present embodiment, operating member 30 moves second ring gear 1322 via a connecting member in the housing between the first shift position and the second shift position in the drill mode. Preferably, the coupling assembly includes a circular arc shaped shift wire 41 and a slider 42 that couples the shift wire 41 and the operating member 30 and is axially movable by the operating member 30.

Two free ends of the shift wire 41 are respectively located in the annular groove 1326 of the second ring gear 1322 to move the second ring gear 1322 through the shift wire 41. The slider 42 is drivingly connected between the operating member 30 and the shift ring gear (i.e., the output ring gear 1582) in the axial direction of the drive shaft, and the gear housing is provided with a slide rail 1125 for the slider 42 to move axially in order to allow the slider 42 to move along a predetermined path in the housing. Preferably, the slider 42 is disposed intermediate the free ends of the shift wire 41, and the shift wire 41 is pivotally connected to the gearbox housing intermediate the slider 42 and the free ends. In the present embodiment, the operating member 30 and the sliding member 42 can rotate relatively, that is, the operating member 30 can rotate relative to the sliding member 42 to switch the screwdriver from the drill mode to the auto chuck mode. Preferably, the sliding member 42 is provided with a mode switching groove 421 along the circumferential direction, the front end of the operating member 30 is provided with a guide block 300 which is matched with the mode switching groove 421, and when the operating member 30 is switched between the high-speed position and the low-speed position, the guide block 300 drives the sliding member 42 to axially move through the mode switching groove 421; when the operating member 30 is rotated in the low-speed position, that is, the operating member 30 moves along the second sliding slot 312 and the third sliding slot 313 in the low-speed position, the guide block 300 can rotate in the mode switching slot 421 to rotate the operating member 30 relative to the sliding member 42 to complete the mode switching.

Preferably, the mode selection mechanism further comprises a switching ring 43, a guide member (not shown), a push rod assembly 45 and the locking member 130, wherein the switching ring 43 is sleeved outside the gearbox housing and can be driven to rotate by the operating member 30, the locking member 130 can both lock the body 151 and the output inner gear ring 1582, and preferably, a slot 431 is formed in the switching ring 43, so that the operating member 30 can axially move along the slot 431 to realize switching between a high-speed position and a low-speed position in a drill mode; when the operating member 30 moves along the second runner 312 in the low-speed position, that is, the operating member 30 performs circumferential rotation, the operating member 30 circumferentially abuts the shift ring 43 during rotation to rotate the shift ring 43 together.

The switch ring 43 is provided with a guide slot, and when the hand-held power tool is switched from the drilling mode to the chuck adjusting mode, the switch ring 43 rotates around the axis of the driving shaft under the action of the operating member 30 and drives the connecting member and the locking member to axially move through the guide slot and the push rod assembly 45.

Specifically, the switching ring 43 is provided with a first guide groove 4321 and a second guide groove 4322. The push rod assembly 45 includes a first push rod assembly 451 connected to the locking member 130 and a second push rod assembly 452 connected to the output ring gear 1582, and preferably, the guide member is a switching pin including a first switching pin 4514 connecting the first push rod assembly 451 and the first guide groove 4321 and a second switching pin 4524 connecting the second push rod assembly 452 and the first guide groove 4322.

Referring to fig. 8-11 and 18-21, when the operating member 30 is switched from the position shown in fig. 10 to the position shown in fig. 8, that is, from the park mode low-speed state to the auto chuck mode with the jaws 152 opened, the switching ring 43 rotates with the operating member 30 in the direction of arrow L in fig. 11 under the action of the operating member 30, the first guide groove 4321 on the switching ring 43 drives the locking member 130 to move axially rearward through the first switching pin 4514 and the first push rod assembly 451, and the second guide groove 4322 on the switching ring 43 drives the output ring gear 1582 to move axially forward through the second switching pin 4524 and the second push rod assembly 452, so that the body 151 is fixed and the output ring gear 1582 is rotationally connected with the nut sleeve 154. Preferably, in this embodiment, the switching ring 43 is further provided with an opening trigger 433 and a locking trigger 434, and after the output ring gear 1582 and the locking member 130 move to a predetermined position, the opening trigger 433 triggers the motor reversing switch 435, so that the motor drives the nut sleeve 154 to rotate in a predetermined direction to perform an opening action of the clamping jaw 152. Referring to fig. 10-12 and 19-21, when the operating member 30 is switched from the position shown in fig. 10 to the position shown in fig. 12, that is, from the low-speed state in the park mode to the closed state of the clamping jaws 152 in the automatic mode, the switching ring 43, after rotating to the right position, triggers the motor reversing switch 435 through the locking trigger 434 connected thereto, so that the motor drives the nut sleeve 154 to rotate in a predetermined direction to perform the closing action of the clamping jaws 152, and the principle is substantially the same as that when the clamping jaws 152 are opened, and will not be described again.

referring to fig. 23, preferably, the first push rod assembly 451 includes a first link 4513 connected to the first switching pin 4514 and is connected to the locking member 130 through the first link 4513 to move the locking member 130 axially forward and backward. Preferably, the first push rod assembly 451 further comprises a first self-aligning element 4510, wherein the first self-aligning element 4510 comprises a first push rod 4511 connected to a first switching pin 4514, and a first elastic element 4512 disposed at a front end of the first push rod 4511 and between the first push rod 4511 and the first connecting rod 4513. When the first switching pin 4514 moves forward, it can push the first link 4513 to move forward by means of the first push rod 4511 and the first elastic member 4512 located at the front end of the first push rod 4511. Preferably, the first link 4513 extends with a first stopper 4518 (see fig. 1) in front of the first elastic element 4512 in a radial direction, and the first elastic element 4512 abuts against the first stopper 4518. The first link 4513 is provided with an axially extending link slot 4515 (see fig. 20), and the first switching pin 4514 penetrates through the link slot 4515, so that the first switching pin 4514 can drive the first link 4513 to move backward when moving backward under the action of the first guide slot 4321, and provide a space for the first switching pin 4514 to move when the first switching pin 4514 moves forward. The second push rod assembly 452 includes a second connecting rod 4523 connected to a second switching pin 4524, and is connected to the output ring gear 1582 through the second connecting rod 4523 to drive the output ring gear 1582 to move axially back and forth.

Referring to fig. 22, preferably, the second push rod assembly 452 further includes a second self-aligning element 4520, wherein the second self-aligning element 4520 includes a first push rod 4511 connected to a second switching pin 4524, and a second elastic element 4522 disposed at a front end of the second push rod 4521 and between the second push rod 4521 and the second link 4523. When the second switching pin 4524 moves forward, it can push the second link 4523 to move forward by the second push rod 4521 and the second elastic element 4522 at the front end of the second push rod 4521. The second link 4523 extends radially in front of the second elastic element 4522 to form a second stopper 4528 (see fig. 1), and the second elastic element 4522 abuts against the second stopper 4528. The second link 4523 is provided with a second link slot 4525 (see fig. 1) extending axially, and the second switching pin shaft passes through the second link slot 4525, so that the second switching pin shaft 4524 can drive the second link 4523 to move backwards when moving backwards under the action of the second guide slot 4322, and provide a space for the second switching pin shaft 4524 to move forwards when the second switching pin shaft 4524 moves forwards. In the embodiment, when the locking member 130 moves forward to engage with the output ring gear 1582 by arranging the first push rod assembly 451 with the first self-aligning member 4510, and a "tooth jacking" phenomenon occurs, after the output ring gear 1582 rotates by a certain angle, the locking member 130 is smoothly engaged with the output ring gear 1582 in place by the first self-aligning member 4510. It can be understood that when the "tooth jacking" phenomenon occurs during the forward movement of the row output ring gear 1582 to engage with the engagement teeth 211 of the first clutch 21 by providing the second push rod assembly 452 with the second self-aligning member 4520, the output ring gear 1582 is smoothly engaged with the engagement teeth 211 by the second self-aligning member 4520 in place after the output ring gear 1582 is rotated by a certain angle.

referring to fig. 18-21, fig. 18 and 19 are state diagrams of the corresponding relationship between the switching ring 43 and the switching pin in the drill mode, and in fig. 18, the screwdriver is in the high speed state, and in fig. 19, the screwdriver is in the low speed state, fig. 20 and 21 are state diagrams of the corresponding relationship between the switching ring 43 and the switching pin in the autochuck mode, that is, fig. 19 is a state diagram corresponding to fig. 10, fig. 20 is a state diagram corresponding to fig. 8, and fig. 21 is a state diagram corresponding to fig. 12. When the operating member 30 is switched from fig. 10 to fig. 8, the switching ring 43 is rotated from the state shown in fig. 19 to the state shown in fig. 20 according to the arrow B direction in fig. 19, at this time, the first guide groove 4321 drives the first push rod 4511 to move forward through the first switching pin 4514, when the first push rod 4511 moves forward, the first push rod 4511 compresses the first elastic element 4512 and presses the first connecting rod 4513 through the first elastic element 4512 to drive the locking member 130 to move forward through the first connecting rod 4513, meanwhile, the second guide groove 4322 drives the second push rod 4521 to move backward through the second switching pin 4524, and the second push rod 4521 or the second switching pin 4524 drives the second connecting rod 4523 to move backward. When the switch ring 43 is rotated from the state shown in fig. 19 to the state shown in fig. 21 according to the arrow F direction in fig. 19, the first guide groove 4321 drives the first push rod 4511 to move forward through the first switch pin 4514, and when the first push rod 4511 moves forward, the first push rod 4511 compresses the first elastic element 4512 and presses the first link 4513 through the first elastic element 4512 to drive the locking member 130 to move forward through the first link 4513. Referring to fig. 20, preferably, the outer side of the gearbox housing is provided with a first groove 1126 extending axially, a first push rod 4511 and a first resilient member 4512 are located in the first groove 1126 so as to be axially movable along the first groove 1126, and a first link 4513 is located in the first groove 1126 and covers over the first push rod 4511 and the first resilient member 4512. The outer side of the gear box housing is further provided with a second groove 1127 extending axially, a second push rod 4521 and a second resilient member 4522 are located in the second groove 1126 so as to be axially movable along the second groove 1127, and a second link 4523 is located in the second groove 1127 and covers over the second push rod 4521 and the second resilient member 4522. Preferably, there are at least two sets of first pusher bar assemblies 451 and second pusher bar assemblies 452.

it is understood that in other embodiments, the first switch pin 4514 can be directly fixedly connected to the first link 4513, so that the axial movement of the first switch pin 4514 directly drives the first link 4513 to perform the axial movement. However, compared to the above-mentioned connection of the first switching pin 4514 and the first self-aligning member 4510, when the first switching pin 4514 moves forward, the first push rod 4511 abuts against the first resilient member 4512 and further pushes the first link 4513 to move forward through the first resilient member 4512, in this way, after the operation member 30 is operated to a certain position, if the slot 1340 on the locking member 130 is not engaged with the lock 1510 on the first body 151a, i.e. the "tooth top" phenomenon occurs, because of the presence of the first resilient member 4512, after the body 151 rotates, the compressed first resilient member 1322 will continue to push the first link 4513 so that the slot 1340 of the locking member 130 is engaged with the lock 1510 on the first body 151a again.

24-26 illustrate a second embodiment of a screwdriver 10 ' of the present invention, which discloses another way to achieve auto chuck mode in which the body 151 ' is rotationally fixed by the body lock 134 ', while the output ring gear 1582 ' rotates the nut sleeve 154 '; in a drill mode, the body lock 134 ' releases the fixation of the body 151 ', the output inner gear ring 1582 ' is fixed relative to the casing ', the body 151 ' drives the clamping jaw 152 ' to rotate under the driving of the motor so as to drive the tool head to rotate, and the output inner gear ring 1582 ' does not need to move axially during mode switching, so that the output inner gear ring 1582 ' can be stably fixed in the casing, and the output of the screwdriver 10 ' is more stable.

the operating members of this embodiment are different from the first embodiment in that the operating members include a mode operating member 301 'for mode switching and a speed operating member (not shown) for speed adjustment in a drill mode, and the mode selecting mechanism includes the mode operating member 301', a switching ring 43 ', a body lock 134' for locking the body, a third switching pin 4534 ', a third push rod assembly 453', a switching member 182 ', and an inner ring lock 181'. The same as the first embodiment described above is that the body lock 134 ' (the connecting member) is fixed to the housing so as not to be rotatable circumferentially all the time, but is capable of moving axially relative to the housing to switch between a first lock position and a second lock position, the body lock 134 ' being moved axially to switch the body lock 134 ' between the first lock position and the second lock position, and the first lock position being close to the first body 151a ' and the second lock position being far from the first body 151a '. When the screwdriver is in the auto chuck mode, the body lock 134 ' is located at the first locking position, the body lock 134 ' circumferentially and non-rotatably locks the body 151 ' to the machine shell, and when the screwdriver is in the drill mode, the body lock 134 ' is located at the second locking position, the circumferential locking of the first body 151a ' is released by the body lock 134 ', and the output planet wheel 1581 ' can drive the body 151 ' and the clamping jaw 152 ' clamped with the tool head to rotate together.

Preferably, the mode operation member 301 ' is a rotating ring sleeved outside the housing ', the switching ring 43 ' is rotatably connected to the mode operation member 301 ', the switching ring 43 ' is provided with a third guiding groove 432 ', it can be understood that, in other embodiments, the switching ring 43 ' and the mode operation member 301 ' can be integrally formed, that is, the guiding groove 432 ' is provided on the inner wall of the switching ring 43 ', and the guiding groove 432 ' is used for driving the third push rod assembly 453 ' to axially move through the third switching pin 4534 '. One end of the third push rod assembly 453 ' is movably disposed in the third guide groove 432 ' through a third switching pin 4534 ', and the other end is connected to the switching member 182 ' for driving the switching member 182 ' to move axially. The switching member 182 ' is movable between a first switching position close to the ring gear lock 181 ' and a second switching position away from the ring gear lock 181 ', and the switching member 182 ' is rotationally connected to the output ring gear 1582 ' all the time during axial movement. The inner ring gear lock 181 'is fixed relative to the housing in a non-rotatable manner in the circumferential direction, and when the switching member 182' is in the first switching position, the switching member 182 'is rotationally connected with the inner ring gear lock 181' and limits the rotation of the output ring gear 1582 'through the inner ring gear lock 181', that is, the output ring gear 1582 'is fixed relative to the housing' in the circumferential direction at this time; when the switching piece 182 ' is at the second switching position, the switching piece 182 ' is axially separated from the inner ring gear lock 181 ', and the output ring gear 1582 ' can drive the switching piece 182 ' to rotate together.

that is, in the present embodiment, the locking member includes the internal gear lock 181 'and the switching member 182' which are separately provided. The output ring gear 1582 ' is fixed in the switching member 182 ' and moves between a first switching position and a second switching position along with the switching member 182 ', so that the output ring gear 1582 ' is fixed and separated from the ring gear lock 181 '.

In this embodiment, in order to realize that the mode operation member 301 ' enables the third push rod assembly 453 ' to drive the switching member 182 ' to move and the body lock 134 ' can also move to the corresponding position, preferably, the body lock 134 ' is axially abutted against the switching member 182 ' and the body lock 134 ' is further provided with a third elastic element 135 ' between one end far away from the output ring gear 1582 ' and the housing. When the switching member 182 ' moves axially, the switching member 182 ' no longer abuts against the body lock 134 ', the body lock 134 ' can move axially under the action of the third elastic element 135 ', and when the switching member 182 ' moves in the opposite direction, the switching member 182 ' pushes the body lock 134 ' to return to the corresponding position by overcoming the acting force of the third elastic element 135 '.

the principles of switching the screwdriver 10' between the drill mode and the auto chuck mode will be further described below in conjunction with FIGS. 24-26.

Referring to fig. 25, when the screwdriver is in the drill mode, the body lock 134 ' is located at a second lock position away from the first body 151a ', and the body lock 134 ' is axially separated from the first body 151a ', i.e., the body lock 134 ' does not lock the first body 151a ', so that the body 151 ' is rotatably disposed in the housing; meanwhile, the switching member 182 ' is located at the first switching position near the inner ring lock 181 ', the switching member 182 ' is engaged with the ring gear fixing teeth 1811 ' on the inner peripheral wall of the inner ring lock 181 ' through the locking teeth 1821 ' (see fig. 24) located on the outer periphery thereof, and the output ring gear 1582 ' is non-rotatably fixed to the housing, so that the output planet 1581 ' in this mode drives the body 151 ' and the jaws 152 ' to rotate, and further drives the tool bit located in the jaws 152 ' to operate.

when the mode operation member 301 'is rotated to the auto chuck mode, that is, the screwdriver 10' is switched from the state shown in fig. 25 to the state shown in fig. 26, the mode operation member 301 'rotates the switching ring 43', the third push rod assembly 453 'moves the switching member 182' away from the inner ring lock 181 'under the action of the third guide slot 432' of the switching ring 43 ', that is, the switching member 182' moves forward from the first switching position to the second switching position, the locking teeth 1821 'on the outer periphery of the switching member 182' disengage from the ring gear fixing teeth 1811 'on the inner peripheral wall of the inner ring lock 181', and the output ring gear 1582 'can drive the switching member 182' to rotate together relative to the housing. It should be noted that when the switching member 182 ' moves forward from the first switching position to the second switching position, the switching member 182 ' is also connected to the nut sleeve 154 ', so that the nut sleeve 154 ' can be rotated by the rotation of the output ring gear 1582 '. Since the switching member 182 'is axially abutted with the body lock 134', when the switching member 182 'moves forward from the first switching position to the second switching position, the body lock 134' moves from the first locking position away from the first body to the second locking position close to the first body 151a 'by the third elastic element 135', and the body lock 134 'engages with the lock block 1510' on the first body 151a 'through the planet carrier lock teeth (not shown) on the inner peripheral wall thereof to lock the first body 151 a'. Therefore, in this mode, the output ring gear 1582 ' can rotate relative to the fixed first body 151a ' and the jaws 152 ' by the switching member 182 ', thereby achieving the opening or closing motion of the jaws 152 '.

When the mode operation member is rotated continuously, when the screwdriver is switched from the auto chuck mode to the drill mode, the mode operation member 301 'drives the switching ring 43' to rotate, and the rotation of the switching ring 43 'causes the third push rod assembly 453' to overcome the elastic force of the third elastic element 135 'to drive the switching member 182' and the body lock 134 'abutted by the switching member 182' to move backward together, so that the screwdriver returns to the drill mode state. Preferably, in order that the locking teeth 1821 ' of the outer periphery of the switching member 182 ' can smoothly engage with the ring gear fixing teeth 1811 ' of the ring gear lock 181 ' when the switching member 182 ' moves backward from the second switching position to the first switching position, a fourth elastic member (not shown) is provided at the rear side of the ring gear lock 181 ' such that the locking teeth 1821 ' of the outer periphery of the switching member 182 ' and the ring gear fixing teeth 1811 ' of the ring gear lock 181 ' are "top teeth" such that the switching member 182 ' rotates by the ring gear lock 181 ' compressing the fourth elastic member and the ring gear lock 181 ' engages in place after the rotation.

the present embodiment further includes a clutch mechanism 20 ' for interrupting torque transmission between the output ring gear 1582 ' and the nut sleeve 154 ' when the jaws 152 are locked or unlocked, the clutch mechanism 20 ' includes a first clutch member 21 ' rotatably connected to the switching member 182 ' after the switching member 182 ' moves forward, and a second clutch member 22 ' rotatably connected to the nut sleeve 154 ', and a clutch elastic member 23 ' is provided between the first clutch member 21 ' and a housing at a front end thereof. When the holding claws 152 ' are locked or fully opened, the first clutch member 21 ' is moved forward against the elastic force of the clutch elastic member 23 ' to disconnect the torque transmission between the first clutch member 21 ' and the second clutch member 22 '.

Fig. 27-30 show partial cross-sectional views of screwdriver 10 "according to a third embodiment of the present invention, which discloses another way to achieve the rotation fixing of body 151" by body lock 134 "in auto chuck mode, while output ring gear 1582" drives nut sleeve 134 "to rotate, and body lock 134" releases the fixing of body 151 "in drill mode, while output ring gear 1582" is fixed relative to the housing, and body 151 "drives jaws 152" to rotate under the driving of a motor to achieve the rotation of driving tool head.

the mode selection mechanism in this embodiment includes a mode operation member 301 ″, a switch ring (not shown in the drawings) provided with a guide groove (not shown in the drawings), a guide member, a switch member 182 ″, a body lock 134 ″, and an internal gear lock. Preferably, the mode operating member 301 "is a rotating ring sleeved on the outer side of the housing, the guide member includes a third switching pin 4534" for driving the switching member 182 "to move axially, and the guide groove includes a third guide groove 432" for allowing the third switching pin 4534 "to move. Preferably, the switching ring is integrally formed with the mode operating member 301 "in this embodiment, that is, the inner circumferential surface of the mode operating member 301" is provided with a guide groove. One end of the third switching pin 4534 "is movably disposed in the third guide groove 432", and the other end is connected to the switching member 182 "for driving the switching member 182" to move axially. The body lock 134 "is movable, but circumferentially non-rotatable, relative to the cabinet between a first lock position proximate the first body 151 a" and a second lock position distal the first body 151a ". Like the second embodiment described above, the switching member 182 "in this embodiment is always rotationally connected to the output ring gear 1582", the ring gear lock 181 "is non-rotatably fixed to the housing, the switching member 182" is axially moved to engage with or disengage from the ring gear lock 181 "to respectively circumferentially fix or circumferentially rotate the output ring gear 1582", that is, the switching member 182' is movable between a first switching position close to the ring gear lock 181 "and a second switching position away from the ring gear lock 181", and the switching member 182 "is always rotationally connected to the output ring gear 1582" during the axial movement. The inner ring gear lock 181 "is circumferentially fixed relative to the housing in a non-rotatable manner, and when the switching member 182" is in the first switching position, the switching member 182 'is rotationally connected with the inner ring gear lock 181' and limits the rotation of the output ring gear 1582 "through the inner ring gear lock 181", that is, the output ring gear 1582 "is circumferentially fixed relative to the housing at this time; when the switching member 182 "is in the second switching position, the switching member 182" is axially separated from the inner ring gear lock 134', the output ring gear 1582 "can drive the switching member 182" to rotate together, and the switching member 182 "is rotatably connected with the nut sleeve 154".

The main difference between this embodiment and the second embodiment is the structure and movement of the body lock 134 "in this embodiment. The switching pin of this embodiment further includes a fourth switching pin 4516 "connected to the body lock 134" for moving the body lock 134 "in a radial direction, and the guide groove further includes a fourth guide groove (not shown) for moving one end of the fourth switching pin 4516". The other end of the fourth switching pin 4516 "is connected to the body lock 134" for bringing the body lock 134 "into radial movement so that the body lock 134" can lock and unlock the first body 151a ", and preferably, the fourth switching pin 4516" is integrally formed with the body lock 134 "in this embodiment.

Referring to fig. 27, when screwdriver 10 "is in drill mode, body lock 134" is radially separated from first body 151a ", inner ring lock 181" is rotationally connected to output ring gear 1582 "via switching member 182", and switching member 182 "is separated from nut sleeve 154", so that, in this mode, rotation of body 151 "rotates jaws 152" together with the tool head located within jaws 152 ". Referring to fig. 29, when screwdriver 10 "is in auto chuck mode, body lock 134" is radially engaged with first body 151a "to rotationally fix body 151" relative to the housing, while ring gear lock 181 "is disengaged from output ring gear 1582" by switching member 182 ", and switching member 182" is rotationally connected to nut sleeve 154 ", so that, in this mode, output ring gear 1582" can bring switching member 182 "and nut sleeve 154" together to rotate relative to jaws 152 "in body 151" to cause the jaws to perform an opening or closing action.

Referring to fig. 28-29, when the screwdriver 10 "is switched from the drill mode to the auto chuck mode, the switch member 182" is first disconnected from the inner ring lock 181 "during movement, the switch member 182" is connected to the nut sleeve 154 "as the switch member 182" continues to move, and the body lock 134 "is now connected to the body 151 a". It should be noted that, in this embodiment, when the clamping jaw 152 "is opened or locked, the clutch mechanism 20" is disconnected from the output ring gear 1582 "and the nut sleeve 154", unlike the above-mentioned embodiment, the clutch movable end tooth 212 "in this embodiment is fixedly connected to the switching member 182", the clutch fixed end tooth 212 "is fixed to the nut sleeve 154", and the clutch elastic element 23 "is arranged between the switching member 182" and the casing. Referring to fig. 30, when output ring gear 1582 "drives nut sleeve 154" through switching member 182 "in auto chuck mode, so that clamping jaw 152" is clamped or completely opened, switching member 182 "presses clutch elastic element 23", and clutch movable end tooth 212 "is separated from clutch static end tooth 222". Preferably, in order that movement of the switching member 182 "does not result in movement of the third switching pin 4534" connected to the switching member 182 "and the mode operating member 301" when "tripped", the switching member is provided with an axially extending clutch groove 182a "to enable movement of the switching member 182" relative to the third switching pin 4534 "when" tripped ".

Fourth embodiment

fig. 31-42 are schematic views of an electric screwdriver 10a according to another embodiment of the present invention, the screwdriver 10a including a housing, a motor 12a, an output device 15a, a transmission mechanism, and a mode selection mechanism. Specifically, the housing includes a main housing 1101a extending in a horizontal direction and a handle housing 1102a fixedly connected to the main housing 1101a and forming a grip handle, the main housing 1101a includes a rear housing 1103a and a front housing 1104a, and the front housing 1104a and the rear housing 1103a are butted to form a receiving cavity for receiving at least part of the output device 15 a.

The motor 12a is disposed in the housing, and outputs rotational power. The output device 15a includes an output shaft 150a, and the output shaft 150a is provided with a receiving hole 1500a for receiving a tool bit. A transmission mechanism is located between the motor 12a and the output device 15a to transmit the rotational power of the motor 12a to the output device 15 a. The mode selection mechanism is used to switch the screwdriver 10a between at least a drilling mode or a chuck adjustment mode.

Referring to fig. 31-36, the output shaft 150a includes a body 151d, a clamping jaw 152a disposed around the receiving hole for clamping the tool bit, and a clamping groove 153a disposed on the body 151a for receiving the clamping jaw 152a, the output device 15a further includes an output planet 1581a, an output ring gear 1582a disposed outside the output planet 1581a, and an adjusting ring disposed outside the body 151a and capable of rotating relative to the body 151a and the clamping jaw 152a to lock or unlock the clamping jaw 152a, basically, as in the previous embodiment, the adjusting ring includes a nut sleeve 154a, an internal thread (not shown) is provided on the inner circumferential wall of the nut sleeve 154a, an external thread 1521a is provided on the side of the clamping jaw 152a facing the internal thread, as the nut sleeve 154a is rotated relative to the jaw 152a, the interaction between the internal threads and the external threads 1521a causes the jaw 152a to perform an opening or closing action. The transmission mechanism is provided with an output sun gear 1583a for driving the output planet gear 1581a to rotate.

The mode selection mechanism includes a connector 420a capable of connecting the output ring gear 1582a and the adjustment ring, and a lock member 130a capable of selectively preventing rotation of the output ring gear 1582a or the body 151d, the lock member 130a being non-rotatably provided with respect to the housing.

when the tool head is in the drilling mode, the locking element 130a is connected with the output inner gear ring 1582a to prevent the output inner gear ring 1582a from rotating circumferentially, and the output inner gear ring 1582a and the adjusting ring are disconnected under the action of the connecting piece 420a, so that the body 151d and the clamping jaw 152a can rotate under the driving of the motor to drive the tool head to perform work; when the screwdriver 10a is switched from the drilling mode to the chuck adjusting mode, the locking element 130a is connected with the body 151a and is separated from the output inner gear ring 1582a to prevent the body 151a from rotating circumferentially and release the circumferential limitation on the output inner gear ring 1582a, and the output inner gear ring 1582a and the adjusting ring are connected under the action of a connecting piece, so that the output inner gear ring 1582a can drive the adjusting ring to rotate relative to the body 151d and the clamping jaws 152a under the action of the motor 12a to realize the opening or closing of the clamping jaws 152 a. Therefore, as in the first embodiment described above, locking member 130a in the present embodiment includes both the body lock for locking body 151a and the ring gear lock for locking output ring gear 1582a, in other words, the body lock for locking body 151a is inseparably connected or integrally formed with the ring gear lock for locking output ring gear 1582a, unlike the first embodiment described above, the present embodiment is implemented by providing connector 420a such that output ring gear 1582a and the adjustment ring are connected in the rotational direction in the autochuck mode, but output ring gear 1582a and the adjustment ring are disconnected in the rotational direction instead of axially moving output ring gear 1582a in the drill mode, and therefore, the fixation of output ring gear 1582a with respect to the housing can be more stabilized, thereby making the output system also more stable.

In this embodiment, the mode selection mechanism further includes a first push rod assembly 451a connected to the locking element 130a for pushing the locking element 130a to move so as to selectively lock the body 151d or output the inner ring gear 1582a by the locking element 130a, and a fourth push rod assembly 454a connected to the first push rod assembly 451a and the connecting member 420a, so that the fourth push rod assembly 454a can drive the connecting member 420a to move under the action of the first push rod assembly. Preferably, in the present embodiment, the locking member 130a is moved in the axial direction to switch the locking member 130a between the first locking position and the second locking position, and the link 420a is moved in the axial direction to switch the link between the first connecting position and the second disconnecting position.

How first push rod assembly 451a moves fourth push rod assembly 454a and link 420a connected to fourth push rod assembly 454a will be further described below in conjunction with fig. 31 and 37-39. The first push rod assembly 451a includes a first link 4511a, wherein one end of the first link 4511a is connected to the connecting member 420a, and the other end is connected to the locking element 130a, and when the screwdriver is switched from the drill mode to the automatic mode, the first link 4511a drives the locking element 130a to move forward in the axial direction under the action of external force. The fourth push rod assembly 454a includes a fourth link 4541a, in order to enable the first link 4511a to drive the fourth link 4541a to move axially forward, a push rod elastic member 480a is further disposed between the first push rod assembly 451a and the fourth link 4541a, wherein the first push rod assembly 451a first drives the locking element 130a to move axially forward, and the forward movement of the first push rod assembly 451a causes the push rod elastic member 480a to compress and push the fourth link 4541a to move forward through the push rod elastic member 480a after the push rod elastic member 480a is compressed to a certain extent. By arranging the push rod elastic member 480a between the first push rod assembly 451a and the fourth connecting rod 4541a, after the first locking element 130a is separated from the body 151a ', the fourth connecting rod 4541a drives the connecting member 420a to move to connect the output ring gear with the adjusting ring, that is, the push rod elastic member 480a prevents the output ring gear 1582a from being connected with the adjusting ring before the first locking element 130a is not separated from the body 151 a' and causes an abnormal condition.

When the screwdriver is switched from the auto chuck mode to the drill mode, that is, the first link 4511a moves backward under the action of an external force, and at this time, the first link 4511a drives the locking element 130a to move backward in the axial direction. In order to enable the first link 4511a to drive the fourth link 4541a to move axially backwards, one of the first link 4511a or the fourth link 4541a is provided with an axially extending link guide groove 4510a, and the other of the first link 4511a or the fourth link 4541a is provided with a link guide 4542a located in the link guide groove 4512a, in this embodiment, the link guide groove 4512a is located in the first link 4511a, and the link guide 4542a is located in the fourth link 4541 a. When the first link 4511a moves axially rearward, the link guide 4542a abuts against the link guide groove 4512a, and thus the first link 4511a brings the fourth link 4514a into axial rearward movement, thereby achieving mode switching.

referring to fig. 34 and 35, when the screwdriver is in auto chuck mode, locking member 130a is in the first locking position, link 420a is in the link position, and locking member 130a circumferentially non-rotatably locks body 151d to the housing while link 420a connects output ring gear 1582a to the adjustment ring. Referring to fig. 32-33, when in the drill mode, the locking element 130a is located at the second locking position, the locking element 130 releases the circumferential locking of the body 151d and circumferentially locks the output ring gear 1582a through axial movement, and at the same time, the connecting element 420a disconnects the output ring gear 1582a from the adjusting ring, and the output planet gears 1581a can drive the body 151d and the clamping jaws 152a located in the body 151d to rotate together.

the screwdriver 10a further includes a clutch mechanism 20a between the adjustment ring and the output ring gear 1582a for disconnecting torque transmission between the output ring gear 1582a and the adjustment ring in the auto chuck mode after the jaws 152a are opened or closed, the clutch mechanism 20a includes a first clutch member 21a capable of being rotatably connected with the output ring gear 1582a, and a second clutch member 22a rotatably connected to the adjustment ring and axially movable relative to the adjustment ring, and a clutch elastic member 23a, in this embodiment, the clutch elastic member 23a is located between the second clutch member 22a and the front housing 1104a, when the jaws 152a are clamped or fully opened, the second clutch member 22a compresses the clutch elastic member 23a, the second clutch member 22a moves axially forward, the first clutch member 21a is disengaged from the second clutch member 22a, and the output ring gear 1582a no longer transmits torque to the adjustment ring (the nut sleeve 154 a). Preferably, the first clutch member 21a is a snap ring sleeved on the periphery of the body 151 a', the snap ring is provided with a clutch tooth groove 211a extending axially, the connecting member 420a is provided with a connecting tooth 421a engaged with the tooth groove 211a, in this embodiment, the connecting member 420a is normally engaged with the first clutch member 21a, that is, the connecting tooth 421a is always located in the clutch tooth groove 211a, and the first clutch member 21a is connected to the output ring gear 1582a by the connecting tooth 421a moving axially backward in the clutch tooth groove 211a, that is, moving axially closer to the output ring gear 1582 a. Of course, it is understood that in other embodiments, the clutch structure 20a may be disposed in other ways, such as, for example, the elastic clutch element 23a is located between the first clutch member 21a and the housing 11a, when the clamping jaws 152a are clamped or completely opened, the first clutch member 22a compresses the elastic clutch element 23a, the first clutch member moves axially, the first clutch member 21a is disengaged from the second clutch member 22a, and the output ring gear 1582a no longer transmits torque to the nut sleeve 154 a.

In this embodiment, the mode selection mechanism further includes a mode operating member 301a, and the mode operating member 301a and the first push rod assembly 451a are connected to transmit the movement of the mode operating member 301a to the first push rod assembly 451 a. in this embodiment, in order to facilitate the switching of the mode when the operator holds the handle housing 1102a with one hand, the mode operating member 301a is disposed adjacent to the handle housing 1102a so that the operator can hold the handle and control the linear movement of the mode operating member 301a with one hand. Preferably, in this embodiment, when the screwdriver is switched to the autochouck mode, the mode operation member 301a is moved in a first direction by pressing with a finger, and preferably, the output shaft 150a has a first end provided with the receiving hole 1500a and a second end opposite to the first end along the axial direction, and the first direction is a direction from the first end to the second end, that is, the mode operation member 301a has an initial position and a switching position after being moved to a position from the initial position along the first direction, so that the screwdriver is in the autochouck mode after the mode operation member 301a is moved to the switching position along the first direction. In addition, the middle mode selection mechanism of the present embodiment further includes a mode reset element 303a, the mode reset element 303a is located between the mode operation member 301a and the housing, after the mode operation member 301a moves to the switching position along the first direction, the mode reset element 303a is in an elastic energy storage state under the action of an external force through the mode operation member 301a, that is, when the mode reset element 303a is a tension spring, the mode reset element 303a is stretched under the action of the external force, when the mode reset element 303a is a compression spring, the mode reset element 303a is compressed under the action of the external force, and when the external force is released, the mode operation member 301a moves to the initial position under the action of the mode reset element 303 a.

in this embodiment, the screwdriver further includes a switch operating element 304a for controlling power supply or power off of the motor, and a first control component for controlling the motor to move according to movement of the switch operating element 304a, so as to facilitate control of the motor speed when the switch operating element is operated, and along with different sizes of strokes of movement of the switch operating element, the first control component makes the rotating speeds of the motors different, and when the strokes are larger, the rotating speeds of the motors are higher. In substantially the same manner as the mode operation member 301a in this embodiment, in order to facilitate the control of the switch operation member when the operator holds the handle with one hand, the switch operation member 304a is disposed adjacent to the handle housing so that the operator can hold the handle and control the movement of the switch operation member with one hand at the same time, the movement of the switch operation member 304a is preferably a linear movement, the switch operation member 304 has a switch initial position for disconnecting the motor from the power supply and an operation position for connecting the motor to the power supply, and the larger the stroke of the switch operation member moving in the first direction, that is, the farther the distance of the operation position from the output position, the higher the rotation speed of the motor.

As can be seen from the above description of the first embodiment, when the screwdriver is in the automatic mode, if the speed of the motor is high, the problem of "trip" sound is harsh and the operating environment is poor is easily caused. To avoid this problem, it is necessary to limit the stroke of the movement of the switch operating member 304a to avoid a higher motor speed due to a larger stroke of the movement of the switch operating member 304. Referring to fig. 32-35, in the present embodiment, the screwdriver further includes a locking mechanism 305a, and the locking mechanism 305a is pivotally disposed on the housing and can be driven by the mode operation member 301a to perform a pivotal movement in a predetermined pivotal direction. When the mode operation member 301a is switched to the switching position, the mode operation member 301a forces the first limit arm 3051 to pivot the locking mechanism 305a to the first limit position, and the free end of the second limit arm 3052a moves between the switch initial position and the switch final operation position, that is, moves to the operation position to limit the movement stroke of the switch operation member, so as to control the rotation speed of the motor, as shown in fig. 35. In order to prevent the mode operation element 301a from being operated by an operator in error in the drill mode, when the switch operation element 304a moves to any operation position, and if the mode operation element 301a is operated, when the mode operation element 301a drives the free end of the first limit arm 3051a to pivot between the initial position and the switching position, the travel switch abuts against the second limit arm 3052a in the preset pivoting direction, and the mode operation element 301a cannot move to the switching position. In this embodiment, a mode connector 302a is further disposed between the locking mechanism 305a and the first link 4511a, and preferably, the mode connector 302a is an elastic steel wire.

Referring to fig. 31 to 34, in the present embodiment, the mode operation member 301a is provided with a mode switching groove 3011a for guiding the free end of the first limit arm 3051a to move, when the mode operation member 301a moves along the first direction, the free end of the first limit arm 3051a moves according to a preset path under the action of the mode switching groove 3011a, the locking mechanism 305a pivots according to a preset direction, and the second limit arm 3052a pivots between the switch end position and the switch initial position, so that the switch operation member 304a cannot move from the switch initial position to the switch end position; referring to fig. 34, after the switch operating member 304a is switched from the initial position to the switch final position in the drill mode, the free end of the second limit arm 3052a abuts against the switch operating member 304a in the predetermined rotational direction, that is, the free end 3052a of the second limit arm cannot be pivoted between the switch final position and the switch initial position beyond the switch final position, and therefore, the locking mechanism 305a cannot be pivoted to the first limit position in the predetermined direction.

In other embodiments of the present invention, the locking mechanism 305a may be provided by other mechanisms, as shown in fig. 40-42, the locking mechanism 305a 'is pivotally provided on the housing and can be pivotally moved in a predetermined pivotal direction by the mode operating member 301 a'. The locking mechanism 305a 'includes a first limit arm 3051 a' and a second limit arm 3052a ', and when the mode operator 301 a' is switched to the switching position, the mode operator 301a 'forces the first limit arm 3051' to pivot the locking mechanism 305a 'to the first limit position, and the free end of the second limit arm 3052 a' moves between the switch initial position and the switch final position to limit the travel of the switch operator. After the switch operating member 304a ' moves to the end position, the second limit arm 3052a ' abuts against the travel switch in the predetermined pivotal direction, and the mode operating member 301a ' cannot move to the switching position. As shown in fig. 40 to 41, when the mode operation member 301a ' moves in the first direction, the first abutting portion 3011a ' abuts against the first stopper arm 3051a ', and the first stopper arm 3051a ' drives the stopper mechanism 305a ' to pivot in the predetermined direction, the first abutting portion 3011a ' abuts against the first stopper arm 3051a '. The switch operating element 304a ' is provided with a second abutting portion 3041a ' capable of abutting against the second limit arm 3052a ', when the switch operating element 304a ' moves along the first direction, the second abutting portion 3041a ' abuts against the second limit arm 3052a ', the second limit arm 3052a ' drives the locking mechanism 305a ' to reversely pivot in the preset direction, and thus the free end of the first limit arm 3051a ' moves between the initial position and the switching position. When the mode operating member 301a ' moves in the first direction, the first abutment portion 3011a ' abuts the first stopper arm 3051a ', and the mode operating member 301a ' cannot move to the switching position, i.e., the mode operating member 301a ' cannot switch the screwdriver to the autochouck mode. In addition, in this embodiment, the mode link 302a ' is directly coupled to the mode operator 301a ', i.e., the mode link 302a ' is not coupled to the mode operator 301a ' via the limit mechanism 305a '.

In the same manner as the first embodiment described above, the transmission mechanism is a planetary gear reduction mechanism 13a in this embodiment, wherein the planetary gear reduction mechanism 13a is preferably a two-stage planetary gear reduction mechanism including a first-stage planetary gear train 131a close to the motor and a second-stage planetary gear train 132a close to the output device 15 a. The first-stage planetary gear set 131a includes a first sun gear 1310a fixed to the motor shaft 121a, a first planet gear 1311a engaged with the first sun gear 1310a and disposed at an outer circumference of the first sun gear 1310a, a first ring gear 1312a engaged with the first planet gear 1311a, and a first carrier 1313a for supporting the first planet gear 1311a, and the second-stage planetary gear set 132a includes a second sun gear 1320a fixedly disposed on the first carrier 1313a, a second planet gear 1321a engaged with the second sun gear 1320a, a second ring gear 1322a engaged with the second planet gear 1321a, and a second carrier 1323a for supporting the second planet gear 1321 a. Second ring gear 1322a is movable relative to the housing along motor output shaft 121a between a first shift position close to the motor and a second shift position away from the motor. When the second ring gear 1322a is located at the first shift position, the second ring gear 1322a is rotatably disposed in the housing, and the second ring gear 1322a is engaged with the first planet carrier 1313a and the second planet gear 1321a at the same time, so that the first planet carrier 1313a, the second planet gear 1321a and the second ring gear 1322a rotate together, the second-stage planetary gear set 132a has no speed reduction output, that is, the second planet carrier 1323a rotates at the same speed as the first planet carrier 1313a, and the second planet carrier 1323a outputs high speed. When the second ring gear 1322a is located at the second shift position, the second ring gear 1322a is circumferentially fixed to the rear housing 110a in a non-rotatable manner, and the second ring gear 1322a is disengaged from the first carrier 1313a during axial movement but the second ring gear 1322a is still engaged with the second planet gears 1321a, so that the second carrier 1323a outputs at a predetermined reduction gear ratio with respect to the first carrier 1313a, and the second carrier 1323a outputs a low speed.

In this embodiment, the mode operation member 301a is provided with a switch trigger (not shown in the figure), when the mode switching member moves to the switching position, the switch trigger is triggered, the power supply circuit of the motor is turned on, and the motor drives the adjusting ring to rotate relative to the body 151d to open or close the clamping jaw. In the first embodiment, in order to ensure that the rotation speed of the output shaft 15 is low in the auto chuck mode, the second carrier outputs a low speed in the auto chuck mode by providing the "T" groove structure. In this embodiment, in order to ensure that the rotation speed of output shaft 15a is low in the autochouck mode, screwdriver 10a further includes a position sensor 24a and a second control component, where position sensor 24a is configured to detect the position of second ring gear 1322a and transmit a position signal of second ring gear 1322a to the second control component, and the second control component controls the rotation speed of the motor according to the position of second ring gear 1322a, so that output shaft 15a can always be in the autochouck low-speed mode output in the autochouck mode, that is, output at a speed lower than a preset speed. It should be noted that the autochuk low speed mode in the present embodiment is not a specific value, as long as the speed of the output shaft 15a is lower than the preset rotation speed value.

Fifth embodiment

Fig. 43-53 are schematic views of a fifth embodiment of a screwdriver 10b of the present invention, the screwdriver 10b including a housing, a motor 12b, a battery for supplying power, a transmission, and a collet assembly including a collet housing (front housing) 1104b and an output device 15b at least partially within the collet housing 1104 b. Specifically, the housing includes a rear housing 1103b extending in a horizontal direction and a handle housing 1102b fixedly connected to the rear housing 1103b to form a grip handle, a collet housing 1104b (front housing) abuts against the rear housing 1103b to form a main housing extending in the horizontal direction, and the main housing forms a housing chamber for housing at least a part of the output device 15 b.

the motor 12b is provided in the housing, and outputs rotational power. The output device 15b includes an output shaft 150b, and the output shaft 150b is provided with a receiving hole 1500b for receiving a tool bit. The transmission mechanism is located between the motor 12b and the output device 15b to transmit the rotational power of the motor 12b to the output device 15 b. The mode selection mechanism is used to switch the screwdriver 10b between at least a drilling mode or a chuck adjustment mode.

referring to fig. 43-44, the output shaft 150b includes a body 151b, a clamping jaw (not shown) disposed around the receiving hole 1500b for clamping the tool bit, and a clamping groove 153b disposed on the body 151b for receiving the clamping jaw, the output device 15a further includes an output planet wheel 1581b, an output ring 1582b disposed outside the output planet wheel 1581b, and an adjusting ring disposed outside the body 151b and capable of rotating relative to the body 151b and the clamping jaw to lock or unlock the clamping jaw, the adjusting ring includes a nut sleeve 154b, an inner circumferential wall of the nut sleeve 154b is provided with an inner thread (not shown), a side of the clamping jaw facing the inner thread is provided with an outer thread, and when the nut sleeve 154b rotates relative to the clamping jaw, an interaction between the inner thread and the outer thread causes the clamping jaw to perform an opening or closing action. The transmission mechanism is provided with an output sun gear 1583b for driving the output planet gear 1581b to rotate.

Referring to fig. 43 to 50, the mode selection mechanism includes a coupling member 420b capable of coupling the output ring gear 1582b and the adjustment ring and a lock member 130b capable of selectively preventing the output ring gear 1582b or the body 151b from rotating by moving in the axial direction of the motor shaft by the mode selection member 301 b. The locking member 130b is non-rotatably arranged with respect to the housing. When the drilling tool is in a drilling mode (see fig. 43-46), the locking element 130b is separated from the body 151b and is connected with the output gear 1582b to prevent the output gear 1582b from rotating circumferentially, and power between the output gear 1582b and the adjusting ring is disconnected under the action of the connector 420b, so that the body 151b and the clamping jaws can rotate under the driving of the motor 12b to drive the tool head to perform work; when the screwdriver 10b is switched from the drilling mode to the chuck adjusting mode (see fig. 47-50), the locking element 130b is connected with the body 151b and disconnected with the output ring gear 1582b to prevent the body 151b from rotating circumferentially and remove the circumferential limitation on the output ring gear 1582b, and the output ring gear 1582b and the adjusting ring are connected under the action of the connector 420b, so that the output ring gear 1582b can drive the adjusting ring to rotate relative to the body 151b and the clamping jaws under the action of the motor 12b to realize the opening or closing of the clamping jaws. Thus, as in the first embodiment described above, the locking member 130b in this embodiment comprises both a body lock for locking the body 151b and an inner ring lock for locking the output ring gear 1582b, in other words, the body lock for locking the body 151b is inseparably connected or integrally formed with the inner ring lock for locking the output ring gear 1582b, unlike the first embodiment described above, this embodiment is achieved by providing the connector 420b such that in the autochuck mode, the output ring gear 1582b and the adjustment ring are connected in the rotational direction, but in the drill mode, the output ring gear 1582b and the adjustment ring are disconnected in the rotational direction, rather than by axially moving the output ring gear 1582 b.

referring to fig. 51, the mode selection mechanism includes a bracket 140 slidably disposed on the housing, a first push rod assembly 451b and a mode connection member 302 b. The bracket 140 includes a first sliding section 1401 extending in the axial direction of the motor shaft and a second sliding section 1403 provided perpendicular to the first sliding section 1401. The mode connector 302b is disposed between the second sliding section 1403 and the first push rod assembly 451b, and is linked with the first push rod assembly 451b to transmit the motion of the mode selector 301b to the first push rod assembly 451b, so as to switch the modes of the hand-held power tool.

In this embodiment, the second sliding section 1403 of the bracket 140 faces away from the U-shape of the first sliding section 1401, the first push rod assembly 451b is connected to the open end of the second sliding section 1403 in a matching manner, and the mode connecting member 302b is a U-shaped elastic steel wire with an opening facing the first push rod assembly 451b, and drives the first push rod assembly 451b to link the locking element 130b and the connecting member 420b under the action of external force.

The first push rod assembly 451b includes a first link 4513b and a mode connector 302b for connecting the first link 4513b to one end of the first link 4513b, and the other end is connected to the locking member 130b and the connector 420b together, so as to drive the locking member 130b and the connector 402b to move back and forth in a synchronous axial direction.

As with the fourth embodiment, referring to fig. 43-46, when the screwdriver 10b is in the drill mode, the locking member 130b is disengaged from the engaging teeth (not shown) on the body 151b and engages with the engaging teeth portion (not shown) of the output ring gear 1582b, and the output ring gear 1582b is fixed relative to the housing; at the same time, the attachment 420b is disengaged from the output ring gear 1582 b.

referring to fig. 47-48, when the screwdriver 10b is switched from the drill mode to the auto chuck mode, the locking element 130b and the connector 420b are moved axially rearward by the first link 4513b, and after the locking element 130b is disconnected from the output ring gear 1582b, the locking element 130b continues to move into engagement with the engagement teeth on the body 151b, and accordingly, the connector 420b engages with the engagement teeth of the output ring gear 1582 b.

it should be noted that, in order to avoid the phenomenon that the motor 12b is locked when the coupling 420b is engaged with the output ring gear 1582b when the locking member 130b is not yet disengaged from the output ring gear 1582b, in the present embodiment, the axial distance d1 between the coupling 420b and the output ring gear 1582b is preferably greater than or equal to the axial length L1 of the output ring gear 1582 b. Preferably, the axial distance d1 between the connector 420b and the output ring gear 1582b in the present embodiment is equal to or greater than the axial length L1 of the output ring gear 1582a, which means that the distance from the side of the connector 420b close to the output ring gear 1582b to the side of the locking element 130b close to the output ring gear 1582b is d1, the distance between two side end faces of the output ring gear 1582b in the axial direction is L1 (not shown in the figure), and d1 is equal to or greater than L1. Where d1 is equal to or greater than L1 to avoid stalling of the motor 12b when the coupling 420b engages the output ring gear 1582b when the locking member 130b has not disengaged the output ring gear 1582b, it will be appreciated that in other embodiments the axial spacing d1 between the coupling 420b and the output ring gear 1582b is equal to or greater than the axial length L1 of the output ring gear 1582 a. it will also be appreciated that the axial spacing between the coupling 420d and the locking member 130d is such that the engagement teeth of the output ring gear 1582d do not simultaneously engage the engagement teeth of the coupling 420d and the engagement teeth of the locking member 130 d.

Referring to fig. 49-50, when the screwdriver 10a is switched to the auto chuck mode, the locking member 130a disengages from the meshing teeth of the output ring gear 1582a and engages with the meshing teeth on the body 151a, the body 151a is locked in the rotational direction, and the connector 420a connects both the output ring gear 1582a and the first clutch 21a, so that the adjustment ring can be rotated relative to the body to effect opening or closing of the jaws.

Referring again to fig. 43-50, the screwdriver 10b further includes a clutch mechanism 20b disposed between the adjusting ring and the output ring 1582b for disconnecting torque transmission between the output ring 1582b and the adjusting ring in auto-chuck mode after the jaws are opened or closed, the clutch mechanism 20b includes a first clutch member 21b rotatably connected to the output ring 1582b, a second clutch member 22b rotatably connected to the adjusting ring and axially movable relative to the adjusting ring, and a clutch elastic member 23 b. In this embodiment, the clutch spring 23b is located between the second clutch 22b and the chuck housing 1104b (front housing), and when the jaws are clamped or fully open, the second clutch 22b compresses the clutch spring 23b, the second clutch 22b moves axially forward, the first clutch 21b disengages from the second clutch 22b, and the output ring gear 1582b no longer transmits torque to the adjuster ring (nut sleeve 154 a). Preferably, the first clutch member 21b is a snap ring sleeved on the outer periphery of the body 151b, the snap ring is provided with a clutch tooth groove (not shown, refer to fig. 31 in particular) extending axially, and the connecting member 420b is provided with a connecting tooth (not shown, refer to fig. 31 in particular) engaged with the clutch tooth groove. In this embodiment, the connection member 420b is normally engaged with the first clutch member 21b, that is, the connection teeth are always located in the clutch tooth space, and the connection between the first clutch member 21b and the output gear ring 1582b is realized by the connection teeth moving axially backward in the clutch tooth space, that is, moving axially toward the direction close to the output gear ring 1582 b. Of course, it is understood that the clutch structure 20b may be disposed in other ways in other embodiments, such as the elastic clutch member 23b is located between the first clutch member 21b and the housing 11b, when the jaws are clamped or completely opened, the first clutch member 21b compresses the elastic clutch member 23a, the first clutch member 21b moves axially, the first clutch member 21b is disengaged from the second clutch member 22b, and the output ring gear 1582b no longer transmits torque to the nut sleeve 154 b.

Referring to fig. 43-50, the mode selection mechanism further includes a mode selector 301b movable relative to the housing between a first position and a second position, the hand-held power tool 10b being in a drilling mode when the mode selector 301b is in the first position; when the mode selector 301b is in the second position, the hand-held power tool 10b is in the chuck adjustment mode; when the mode selector 301b moves from the first position to the second position, the mode selector 301b moves in a direction away from the first end (the output shaft 150b has an end provided with the receiving hole 1500b in the axial direction). In this embodiment, the movement of the mode selector 301b between the first position and the second position is a movement in the axial direction of the motor shaft, i.e., the mode selector 301b moves between the first position and the second position in the front-rear direction of the main housing 1101.

Referring to fig. 51, the mode selection member 301b is pivoted to an end of the first sliding section 1401, which is not connected to the second sliding section 1403, and is exposed out of the handle portion so as to be capable of rotating between an initial position and a first position relative to the bracket 140. Specifically, one of the mode selector 301b and the main body is provided with a latch 3010, and the other is provided with a latch groove (not shown).

with continued reference to fig. 43-50, when the mode selector 301b is at the initial position, the latch 3010 is engaged with the slot, and the mode selector 301b is locked with respect to the housing and cannot pivot with respect to the bracket 140, so as to prevent the mode selector 301b from being easily activated by accidental touch. When the mode selector 301b is switched from the initial position to the first position, the latch 3010 is disengaged from the limit of the latch, and the mode selector 301b can be normally actuated by an external force to move between the first position and the second position, so that the handheld power tool can be switched between at least the drilling mode and the chuck adjusting mode.

the mode selection mechanism further comprises a first return elastic member (not shown) which is connected between the bracket 140 and the housing in a deformable manner, and is used for storing energy when the hand-held power tool is switched from the drill mode to the auto chuck mode; when the hand-held power tool is switched from the auto chuck mode to the drill mode, the first return elastic element releases energy, and the driving mode selection element 301b moves from the second position to the first position, so that the hand-held power tool drill mode is switched.

Specifically, when the mode selector 301b moves from the first position to the second position under the action of an external force, the first sliding section 1401 and the second sliding section 1403 are synchronously linked in the same direction (i.e. move backward), so as to drive the first link 4513b to drive the locking element 130b and the link 420b to move backward in the axial direction. At this time, the first return elastic element is charged, the locking element 130b is connected with the body 151b in the rotation direction, the body 151b is locked, and the connecting member 420b is axially moved backward and then connected with the output ring gear 1582b, so that the screwdriver is switched to the auto chuck mode.

when the external force disappears, the first elastic restoring member releases energy, the bracket 140 moves from the back to the front under the action of the elastic force, and the driving mode selecting member 301b moves from the second position to the first position under the action of the elastic force, and drives the first link 4513b to drive the locking member 130b and the connecting member 420b to move axially forward. At this time, the connecting piece 420b is located on the side, away from the motor 12b, of the output gear ring 1582b and is connected with the adjusting ring in a non-relative-rotation mode, the locking element 130b is located at the second locking position, the locking element 130b releases circumferential locking on the body 151b through axial movement and circumferentially locks the output gear ring 1582b, meanwhile, the connecting piece 420b is disconnected between the output gear ring 1582b and the adjusting ring, and the output planetary gear 1581b can drive the body 151b and the clamping jaws located in the body 151b to rotate together.

the transmission mechanism is located between the motor 12b and the output device 15b, and comprises a gear ring gear capable of shifting in a shaft mode so that the transmission mechanism can output at least two different first transmission ratios and second transmission ratios, and the handheld power tool at least has a low speed position corresponding to the first transmission ratio and a high speed position corresponding to the second transmission ratio.

in the same manner as the first embodiment, the transmission mechanism is a planetary gear reduction mechanism 13b, and the planetary gear reduction mechanism 13b is preferably a two-stage planetary gear reduction mechanism including a first-stage planetary gear train adjacent to the motor and a second-stage planetary gear train adjacent to the output device 15 b. The first-stage planetary gear set 131b includes a first sun gear 1310b fixed to the motor shaft 121b, a first planet gear 1311b engaged with the first sun gear 1310b and disposed at an outer periphery of the first sun gear 1310b, a first ring gear 1312b engaged with the first planet gear 1311b, and a first planet carrier 1313b for supporting the first planet gear 1311b, and the second-stage planetary gear set 132b includes a second sun gear 1320b fixedly disposed on the first planet carrier 1313b, a second planet gear 1321b engaged with the second sun gear 1320b, a second ring gear 1322b engaged with the second planet gear 1321b, and a second planet carrier 1323b for supporting the second planet gear 1321 b. Second ring gear 1322b (i.e., equivalent to a shift ring gear in the present embodiment) is movable along 121b with respect to the housing between a first shift position close to the electric motor and a second shift position away from the motor. When the second ring gear 1322b is located at the first shift position, the second ring gear 1322b is rotatably disposed in the housing, and the second ring gear 1322b is engaged with the first planet carrier 1313b and the second planet gear 1321b at the same time, so that the first planet carrier 1313b, the second planet gear 1321b and the second ring gear 1322b rotate together, the second-stage planetary gear set 132b does not output a reduced speed, that is, the second planet carrier 1323b rotates at the same speed as the first planet carrier 1313b, and the second planet carrier 1323b outputs a high speed. When the second ring gear 1322b is located at the second shift position, the second ring gear 1322b is circumferentially fixed to the rear housing 110b in a non-rotatable manner, and the second ring gear 1322b is disengaged from the first carrier 1313b during axial movement but the second ring gear 1322b is still engaged with the second planet gears 1321b, so that the second carrier 1323b outputs at a predetermined reduction gear ratio with respect to the first carrier 1313b, and the second carrier 1323b outputs a low speed. Meanwhile, when the mode selector 301b moves from the first position to the second position, the second ring gear 1322b (i.e., the shift ring gear) can be moved to the first shift position.

referring to fig. 51-53, in the embodiment, when the mode selector 301b is switched from the first position to the second position (i.e. the handheld power tool is switched from the drill mode to the chuck adjusting mode), the mode selector 301b can be synchronously switched to the second speed changing position (i.e. the low speed position) in conjunction with the second annular gear 1322 b; and at the same time, when the mode selecting member 301b returns to the first position, the speed selecting member 1450 drives the second ring gear 1322b to return to the first speed changing position (i.e., the high speed position) under the elastic force of the second restoring elastic member 1451. Therefore, high-speed and low-speed switching is not influenced in the drill mode; when in auto chuck mode, the hand-held power tool is forced to be in low speed operation state, and when returning to drill mode, the original high-low speed gear position is not influenced.

Specifically, the hand-held power tool further includes a speed selecting member 1450 connected to the speed changing ring gear (i.e., the second ring gear 1322b in the present embodiment) to move the speed changing ring gear at the first and second speed changing positions, a second return elastic member 1451 (see fig. 45) located between the housing and the speed selecting member 1450, a main switching member 1452, and an auxiliary switching member 1453.

The speed selection member 1450 is movably coupled to the housing and is movable relative to the housing in an axial direction of the motor shaft by an external force. The main switching member 1452 is rotatable about an axis relative to the housing and is drivingly connected between the speed selecting member 1450 and the speed ring gear for switching the hand-held power tool between at least a low speed position and a high speed position in response to movement of the speed selecting member 1450. The auxiliary switch 1453 has one end connected to the speed selector 1450 and the other end detachably connected to the first link 4513b to forcibly set the hand-held power tool in the auto-chuck mode to the low-speed operation state, and does not affect the original high-low speed gear when returning to the drill mode.

The speed selector 1450 includes a dial button body 14501 and a dial button 14502, the dial button body 14501 is substantially square plate-shaped, and two fitting locations 14503 are arranged along the moving direction of the speed selector 1450, and the main switch 1452 and the auxiliary switch 1453 are sequentially fitted into the fitting locations 14503 along the moving direction of the speed selector 1450 from the high speed location to the low speed location. The dial 14502 includes a button body 14502a and a protrusion 14502b protruding from a surface of the button body 14502a facing the dial body 14501, and the protrusion 14502b is engaged with the mounting portion 14503 of the main switch 14502. When the dial button 14502 moves from the back to the front, the dial button body 14501 is moved by the protrusion 14502b abutting against the main switching piece 14502, and after the dial button body 14501 is moved to the right position, the protrusion 14502b can still limit the main switching piece 14502 to prevent the wrong movement.

The second elastic element 1451 is disposed between the toggle body 14501 and the housing (specifically, the gearbox housing) for providing a restoring force for the speed selecting member 1450 to move from the low-speed position to the high-speed position.

The main switch 1452 includes a first free end 14521 and a second free end 14522 respectively disposed at two sides of its pivot point with respect to the housing. First free end 14521 is connected to speed select member 1450, and second free end 14522 is connected to the speed ring gear; and the first free end 14521 and the second free end 14522 rotate in opposite directions around the pivot point under the action of external force.

specifically, the first free end 14521 is generally arcuate in configuration and is snap-fit within one of the mounting locations 14503. The second free end 14522 is formed by bending the end of the first free end 14521 in an opposite manner and hooked on the shift ring gear to drive the shift ring gear to switch between the first shift position and the second shift position under the action of an external force.

the auxiliary switching element 1453 includes a third free end 14531 and a fourth free end 14532 respectively disposed at two sides of the pivot point between itself and the housing. The third free end 14531 is connected to the speed selector 1450, and the fourth free end 14532 is detachably abutted to the first link 4513 b; and the third free end 14531 and the fourth free end 14532 rotate in opposite directions around the pivot point under the action of external force.

Specifically, the third free end 14531 is generally arcuate in configuration and is snap-fit into one of the mounting locations 14503. The fourth free end 14532 is formed by bending the end of the third free end 14531 away from each other and is located on the moving path of the first link 4513b along the axial direction of the motor shaft.

Preferably, the main switch 1452 and the auxiliary switch 1453 are pivotally connected to the housing in a parallel manner, i.e. the first free end 14521 of the main switch 1452 and the third free end 14531 of the auxiliary switch 1453 are located on the same side of the pivot, and the second free end 14522 of the main switch 1452 and the fourth free end 14532 of the auxiliary switch 1453 are located on the same side of the pivot.

Referring to fig. 43-46, when the hand-held power tool is in the low gear of the drill, the speed selecting member 1450 is located at the front, the first free end 14521 of the main switch 1452 and the third free end 14531 of the auxiliary switch 1453 are located at the side of the respective pivot point close to the first link 4513b, and the second free end 14522 of the main switch 1452 and the fourth free end 14532 of the auxiliary switch 1453 are located at the side of the respective pivot point away from the first link 4513 b. At this time, the fourth free end 14532 of the auxiliary switch 1453 is spaced apart from the end of the first link 4513 b.

When the hand-held power tool is switched from the drill low gear to the auto chuck mode, the mode selector 301b is pressed to drive the first link 4513b to move backward to abut against the fourth free end 14532 of the auxiliary switch 1453, so that the speed selector 1450 cannot be switched from the low gear to the high gear under the action of external force, and the original low gear is always maintained in the auto chuck mode.

when the mode selector 301b is released, the hand-held power tool is returned to the drill mode by the auto-chuck mode through the first return elastic member, and the distal end of the first link 4513b is returned in a direction away from the fourth free end 14532 of the auxiliary switch 1453 and is spaced apart from the fourth free end 14532 of the auxiliary switch 1453. At this time, the main switching member 1452 can be driven by operating the speed selecting member 1450 to freely switch between the high and low gears.

Referring to fig. 47-48, when switching from the drill high gear to the auto-chuck mode, the speed selector 1450 is located at the rear, the first free end 14521 of the main switch 1452 and the third free end 14531 of the auxiliary switch 1453 are located at the side of the respective pivot point away from the first link 4513b, and the second free end 14522 of the main switch 1452 and the fourth free end 14532 of the auxiliary switch 1453 are located at the side of the respective pivot point close to the first link 4513 b. Since the fourth free end 14532 of the auxiliary switch 1453 is located on the moving path of the first link 4513b moving from the forward to the backward direction, when the mode selector 301b is pressed, the first link 4513b is driven to move backward, the first link 4513b will abut against the fourth free end 14532 of the auxiliary switch 1453 to move backward, the fourth free end 14532 of the auxiliary switch 1453 is pivoted to drive the speed selector 1450 to move forward, so that the main switch 1452 is forced to move the speed ring from the first speed-changing position (high speed position) to the second speed-changing position (low speed position), and the auto-chuck mode is ensured to always maintain the low speed position.

When the mode selector 301b is released, the hand-held power tool returns to the drill mode from the auto-chuck mode through the first return elastic member, and the speed selector 1450, which is disengaged from the first link 4513b, returns to the high speed state under the action of the second return elastic member 1451, so that the original high speed gear in the drill state is not changed.

Through the design of the scheme, high-speed and low-speed switching is not influenced when the drill is in the auto chuck mode, the handheld power tool is forced to be in a low-speed running state, and the original high-speed and low-speed gear position is not influenced when the drill mode is recovered.

in the second, fourth and fifth embodiments, although the operation interface is different from the operation interface of the "T" slot in the first embodiment, it is also possible to use the operation interface of the "T" slot in the first embodiment, that is, the operation member for switching speed and the operation member for switching mode in the second, fourth and fifth embodiments may be the same operation member, and the same operation member may realize speed switching and mode switching along different movement traces, and switch to the chuck adjusting mode at a low speed.

The present invention is not limited to the embodiments described in the foregoing embodiments, and other modifications may be made by those skilled in the art within the spirit of the present invention, provided that the functions performed by the present invention are the same or similar to those of the present invention.

Claims

1. A hand-held power tool comprising:

a housing;

a motor disposed in the housing and outputting rotational power;

The operating part is movably assembled on the shell;

A high-low speed switching mechanism capable of switching the hand-held power tool between at least a first speed and a second speed greater than the first speed in response to the operation of the operating member and changing the rotation speed of the drive shaft; the method is characterized in that:

2. the hand-held power tool according to claim 1, wherein the housing defines a slot for the operating member to move, the slot includes a first slot corresponding to the first track and a second slot, and the second slot is communicated with the first slot at a first position so that the operating member can move from the first position to the second slot to switch the hand-held power tool to the chuck adjusting mode.

3. The hand-held power tool of claim 2, wherein the hand-held power tool switches to a chuck adjustment mode in which the jaws are opened when the operating member moves from the first position to the predetermined position along the second slide slot; the sliding groove further comprises a third sliding groove communicated with the first sliding groove at the first position, and when the operating piece moves to a preset position from the first position along the third sliding groove, the handheld power tool is switched to a chuck adjusting mode capable of folding the clamping jaws.

4. the hand-held power tool according to claim 3, wherein the first slide groove extends in the axial direction of the drive shaft on the housing, and the second slide groove and the third slide groove are symmetrically provided on both sides of the first slide groove.

5. The hand-held power tool of claim 2 or 3, wherein the transmission mechanism comprises a speed change ring gear located between the motor and the body, the speed change ring gear being connected to the operator and being axially movable by the operator to cause the transmission mechanism to output at least two different gear ratios to vary the rotational speed of the drive shaft and to enable the hand-held power tool to be switched between a first speed and a second speed.

6. The hand-held power tool according to claim 5, wherein the first slide groove extends in the axial direction of the drive shaft on the housing, and the high-low speed switching mechanism includes a slider drivingly connected between the operating member and the shift ring gear in the axial direction of the drive shaft;

7. the hand-held power tool of claim 1, wherein the mode selection mechanism includes a link and a locking member non-rotatably disposed relative to the housing, the link and the locking member being movable by the operator when the hand-held power tool is switched between the drill mode and the chuck adjustment mode;

8. The hand-held power tool of claim 7, further comprising an output sun gear connected to the drive shaft, an output planetary gear provided on the body and driven by the output sun gear, the connecting member being annular and having an inner peripheral surface provided with inner teeth meshing with the output planetary gear;

9. the hand-held power tool of claim 7, further comprising an output sun coupled to the drive shaft, output planets disposed on the body and driven by the output sun, and an output ring gear in mesh with the output planets;

10. the hand held power tool of claim 9, wherein the locking member is rotationally fixed with the output ring gear in the drill mode to fix the output ring gear relative to the housing.

11. the hand-held power tool of claim 7, wherein the operating member moves along a first path between a first position and a second position in an axial direction of the drive shaft, the mode selection mechanism further comprises a switching ring and a push rod assembly, the switching ring is provided with a guide groove, and when the hand-held power tool is switched from the drilling mode to the chuck adjusting mode, the switching ring rotates around the axis of the drive shaft under the action of the operating member and drives the connecting member and the locking member to move axially through the guide groove and the push rod assembly.

12. The hand held power tool of claim 11, wherein the switch ring defines a slot extending axially along the drive shaft, the operating member being axially movable along the slot when the operating member moves along the first path between the first position and the second position to allow the operating member to move axially along the drive shaft relative to the switch ring.